Automatic transmission for a vehicle

ABSTRACT

An output side transfer member  103  of a second clutch C- 2  extends around the outer circumferences of the output side transfer members  101, 102  of the third and first clutches C- 3 , C- 1 , the output side transfer member  104  (or  13, 101 ) of a fourth clutch C- 4  and the output side transfer member  101  of a third clutch C- 3  are linked to a sun gear S 2 , the output side transfer member  104  (or  13, 101 ) of a fourth clutch C- 4 , an output side transfer member  101  of a third clutch C- 3 , and a sun gear S 2 , which rotate integrally, are disposed radially inward with respect to the output side transfer member  102  of the first clutch C- 1 . Thereby, it becomes possible to reduce the diameter of the output side transfer member  104  (or  13, 101 ) of the fourth clutch C- 4 , to reduce the weight and inertia, and to improve the controllability of the automatic transmission  1.

TECHNICAL FIELD

The present invention relates to an automatic transmission that ismounted in a vehicle or the like, and in particular, relates to aconfiguration for an automatic transmission that enables multi-speedshifting by selectively transferring input rotation and reduced speedrotation to first, second, and third rotary elements of a planetary gearunit by using first and second input transfer clutches and first andsecond speed reduction transfer clutches.

BACKGROUND ART

In recent years, in an automatic transmission that is mounted in avehicle or the like, multi-speed shifting is coming to play a centralrole in satisfying the need to improve fuel economy and the like. Suchan automatic transmission is disclosed, for example, in Japanese PatentApplication Publication No. JP-A-2001-182785 (in particular, refer toFIG. 2 and TABLE 2).

The automatic transmission disclosed in JP-A-2001-182785 is providedwith a speed reduction planetary gear set (G1) that receives the inputrotation that is input to an input shaft (11) and reduces the speed ofthat rotation, first and second input transfer clutches (C4, C3) thatselectively transfers the input rotation, first and second reduced speedtransfer clutches (C2, C1) that selectively transfers rotation at aspeed reduced through the speed reduction planetary gear set (G1), firstand second brakes (B1, B2), that brake the rotation on the case (1), anda planetary gear set (G23) that has at least first, second, third, andfourth rotary elements (S2, S3, PC2 and PC3, R3). This automatictransmission inputs rotation through the first input transfer clutch(C4) to the first rotary element (S2) of the planetary gear set (G23)and the reduced speed rotation is output through the first speedreduction transfer clutch (C2) while the first rotary element (S2) isheld stationary on the case (1) by the first brake (B1). The automatictransmission is structured such that reduced speed rotation can betransferred to the second rotary element (S3) by the second speedreduction transfer clutch (C1). Further, input rotation can betransferred through the second input transfer clutch (C3) to the thirdrotary element combination of (PC2 and PC3) and the third rotary elementcan be held stationary by the second brake (B2). Rotation can be outputfrom the fourth rotary element (R2, R3). Thus, by appropriatelyoperating these clutches (C1, C2, C3, C4) and brakes (B1, B2), theautomatic transmission enables multi-speed shifting.

However, as shown in TABLE 2 of JP-A-2001-182780, while the firstforward speed to the eighth forward speed can be established by suitablyoperating the clutches and brakes, the third rotary elements (PC2 andPC3), which receive the input rotation by engagement of the second inputtransfer clutch (C3), do not attain a speed that is higher than theinput rotation, even if the first rotary element (S2) receives inputrotation by engagement of the first input transfer clutch (C4), because,for example, in the fifth forward speed, the first input transfer clutch(C4) is released, a reduced speed rotation is input to the second rotaryelement (S3) by engagement of the first speed reduction transfer clutch(C1), and rotation is input to the third rotary element (PC2 and PC3) byengagement of the second input transfer clutch (C3), resulting in a highspeed rotation, that is, a speed that is higher than that of the inputrotation.

SUMMARY OF THE INVENTION

In the automatic transmission described above, if the clutches andbrakes were to be disposed farther radially outward from the path bywhich input rotation, through the members (that is, the output sidemember of the first input transfer clutch) that link the first inputtransfer clutch (C4) and the first rotary element (S2), is input to thethird rotary element (PC2 and PC3) via the second input transfer clutch(C3), the members which reach a speed that is higher than the inputrotation, and which therefore require a higher rigidity, would bedisposed radially outward of the members that do not reach a speed thatis higher than that of the input rotation. However, such modificationwould increase centrifugal force in proportion to the increase in thediameter of these members and the thickness of the members must beincreased in order to attain the necessary high rigidity, thusincreasing the weight and the inertia, while reducing thecontrollability of the automatic transmission.

Thus, it is an object of the present invention to provide an automatictransmission for a vehicle that enables a reduction in weight andimprovement in controllability by reducing the inertia.

In the description which follows, the reference numerals in parenthesiswhich refer to the drawing figures, are included by way of example, forconvenience and for understanding of the invention, and should not beinterpreted as limiting the scope of the claims.

Accordingly, the present invention (refer, for example, to FIG. 1through FIG. 19) provides an automatic transmission (1) for a vehiclewhich outputs an output rotation from a fourth rotary element (R3), andwhich has a reduction planetary gear set (DP) that includes a stationaryelement (S1), which is held stationary by the case (4), an input rotaryelement (CR1), which receives the input rotation of the input shaft(12), and a speed reduction rotary element (R1) that outputs a reducedspeed rotation at a speed less than that of the input rotation. Theautomatic transmission of the present invention also has: a planetarygear unit (PU) that includes first, second, third, and fourth rotaryelements (S2, S3, CR2, R3) that have rotational speed relationshipsaccording to their gear relationships; a first input transfer clutch(C-4) for transfer of the input rotation to the first rotary element; asecond input transfer clutch (C-2) for transfer of the input rotation tothe third rotary element (CR2); a first speed reduction transfer clutch(C-3) for transfer of a reduced speed rotation through the speedreduction planetary gear set (DP) to the first rotary element (S2); asecond speed reduction transfer clutch (C-1) for transfer of a reducedspeed rotation through the speed reduction planetary gear set (DP) tothe second rotary element (S3); a first brake (B-1) which, when engaged,locks the first rotary element (S2) against rotation; and a second brake(B-2) which, when engaged, locks the third rotary element (CR2) againstrotation. The output side transfer member (103) of the second inputtransfer clutch (C-2) is linked to the third rotary element (CR2)through the outer circumferential side of the output side transfermembers (101, 102) of the first and second speed reduction transferclutches (C-3, C-1). The output side transfer member (104, 13 in FIG. 8and FIG. 18, 101 in FIG. 15 and FIG. 16) and the output side transfermember (101) of the first speed reduction transfer clutch (C-3) arelinked to the first rotary element (S2). The output side transfer member(104, 13 in FIG. 8 and FIG. 18; 101 in FIG. 15 and FIG. 16) and theoutput side transfer member (101) of the first speed reduction transferclutch (C-3), rotate integrally and are disposed radially inward of anoutput side transfer member (102) of the second speed reduction transferclutch (C-1).

In the above-described automatic transmission of the present invention,because the output side transfer member of the first input transferclutch, which rotates faster than the output side transfer member of thesecond input transfer clutch, is disposed more radially inward than theoutput side transfer member of the second speed reduction transferclutch which, in turn, is radially inward of the output side transfermember of the second input transfer clutch, the diameter of the outputside transfer member of the first input transfer clutch can be madesmaller than the diameter of the output side transfer member of thesecond input transfer clutch, and it is possible to reduce the weight ascompared to a structure in which it is disposed on the outercircumferential side (radially outer side). In addition, in comparisonto a structure in which the output side transfer member of the firstinput transfer clutch is disposed on the outer circumferential side,inertia is reduced and controllability of the automatic transmission isimproved.

In another aspect of the present invention (refer, for example, to FIG.1, FIGS. 5 through 7, FIG. 11 through 14, and FIG. 19), the first andsecond speed reduction transfer clutches (C-3, C-1) are disposed on thespeed reduction planetary gear set (DP) side relative to the planetarygear unit (PU), and the output side transfer members (101, 102) of thefirst and second speed reduction transfer clutches (C-3, C-1) arerespectively linked to the first rotary element (S2) and the secondrotary element (S3). In this embodiment, the first input transfer clutch(C-4) is disposed on the side of the planetary gear unit (PU) axiallyopposite the speed reduction planetary gear set (DP), and the outputside transfer member (104) of the first input transfer clutch (C-4) islinked to the first rotary element (S2). The second input transferclutch (C-2) is disposed on the speed reduction planetary gear set (DP)axial side relative to the planetary gear unit (PU), and the output sidetransfer member (103) of the second input transfer clutch (C-2) islinked to the third rotary element (CR2) on the outer circumferentialside of the output side transfer members (101, 102) of the first andsecond speed reduction transfer clutches (C-3, C-1).

In the preferred embodiment described immediately above, because theoutput side transfer member of the first input transfer clutch, whichreaches a rotational speed that is higher than that of the output sidetransfer member of the second input transfer clutch, is on the radiallyinward side, the diameter of the output side transfer member of thefirst input transfer clutch is smaller than the diameter of the outputside transfer member of the second input transfer clutch, and it ispossible to reduce its weight more than in the case in which it isdisposed on the radially outward side. In addition, because the inertiais reduced in comparison to a structure in which the output sidetransfer member of the first input transfer clutch is disposed on theouter side, it is possible to improve the controllability of theautomatic transmission.

In addition, as compared to a design wherein the hydraulic servo of thefirst input transfer clutch is located between the planetary gear unitand the speed reduction planetary gear set, it is possible to disposethe friction plates of the first input transfer clutch more radiallyoutward, and thus it is possible to enlarge the area of the frictionplates. Therefore, it is possible to ensure transfer of a sufficientamount of torque while reducing the number of friction plates.Furthermore, by shortening the distance between the first and secondspeed reduction transfer clutches and the planetary gear unit, and theoutput side transfer members of the first and second speed reductiontransfer clutches, which must be sufficiently strong to transfer a hightorque, it is possible to reduce weight and to improve thecontrollability of the automatic transmission.

Furthermore, it is possible to supply the working oil to the hydraulicservo of the first input transfer clutch from an oil duct that isprovided, for example, in a boss extending from a side wall of the case.In this manner, as compared to a case in which the working oil issupplied from an oil duct in the input shaft, it is possible to reducethe number of seal rings, to reduce the sliding resistance of the sealrings, and to improve the power transfer efficiency of the automatictransmission.

In addition, in the present invention (refer, for example, to FIG. 1,FIGS. 5 through 7, FIGS. 11 to 14, and FIG. 19), the input side transfermember (52) of the first input transfer clutch (C-4) is linked to theinput shaft (12, 13) radially inward of the planetary gear unit (PU),and a portion of the input side transfer member (52) of the first inputtransfer clutch (C-4) forms the clutch drum (52) of the hydraulic servo(50) of the first input transfer clutch (C-4).

In contrast to transmissions in which a portion of the output sidetransfer member of the first input transfer clutch forms the clutch drumof a hydraulic servo, in the present invention the clutch drum of ahydraulic servo additionally functions as a power transfer member. As aresult, it is possible to make the automatic transmission more axiallycompact.

In another embodiment of the present invention (refer, for example, toFIG. 8, FIG. 15, FIG. 16, and FIG. 18) the first and second speedreduction transfer clutches are disposed on the side of speed reductionplanetary gear set (DP) relative to the planetary gear unit (PU) and theoutput side transfer members (101, 102) of the first and second speedreduction transfer clutches (C-3, C-1) are respectively linked to thefirst rotary element and the second rotary element.

The first input transfer clutch (C-4) is disposed on the side of thespeed reduction planetary gear set (DP) relative to the planetary gearunit (PU) and the output side transfer member (13 in FIG. 8 and FIG. 18,101 in FIG. 15 and FIG. 16) of the first input transfer clutch (C-4) islinked to the first rotary element (S2).

The second input transfer clutch (C-2) is disposed on the speedreduction planetary gear set (DP) relative to the planetary gear unit(PU) and the output side transfer member (103) of the second inputtransfer clutch (C-2) is linked to the third rotary element (CR2)radially outward of the output side transfer members (101, 102) of thefirst and second speed reduction transfer clutches (C-3, C-1).

Thereby, because the output side transfer member of the first inputtransfer clutch, which rotates faster than the output side transfermember of the second input transfer clutch, is on the radially innerside, it is possible to make the diameter of the output side transfermember of the first input transfer clutch smaller than the diameter ofthe output side transfer member of the second input transfer clutch, andto thus reduce the weight as compared to the case in which it is on theradially outer side. In addition, in comparison to a structure in whichit is on the radially outer side, it is possible to decrease theinertia, and to thus improve the controllability of the automatictransmission.

In addition, in the present invention (refer, for example, to FIG. 8,FIG. 15, FIG. 16, and FIG. 18), the input side transfer member (52) ofthe first input transfer clutch (C-4) is directly linked to the inputrotary element (CR1), and along with a portion of the input rotaryelement (CR1), forms a portion of the hydraulic servo (50) of the firstinput transfer clutch (C-4).

Thereby, it is possible to use portions of the members that form theinput rotary element (portions of the clutch drum and the side plate ofthe carrier) and the hydraulic servo of the first input transfer clutchin common, and to thereby reduce the size and weight.

In addition, the present invention (refer, for example, to FIG. 1, FIG.11, FIG. 16, and FIG. 19) may include a boss (3 b) extending from theside wall (3 a) of the case (4) for supporting the stationary element(S1) while holding it stationary.

The input side transfer member (32) of the second input transfer clutch(C-2) is linked to the input rotary element (CR1) and a portion of theinput side transfer member (32) of the second input transfer clutch(C-2) forms the clutch drum (32) of the hydraulic servo (30) of thesecond input transfer clutch (C-2), and that hydraulic servo (30) isdisposed around the boss (3 b), between the speed reduction planetarygear set (DP) and the side wall (3 a).

Supply of the working oil to the hydraulic servo of the second inputtransfer clutch from a duct that is provided in the boss portion, ascompared to supply of working oil via an oil duct in the input shaft,allows the length of the oil duct to be shortened by an amountequivalent to the length of the oil duct in the input shaft.

As shown, for example, to FIG. 1, FIG. 11, FIG. 16 through FIG. 19, theinput side transfer member (111) of the second speed reduction clutch(C-1) is linked to the speed reduction rotary element(s) (R1). Theoutput side transfer member (102) of the second speed reduction transferclutch (C-1) is linked to the second rotary element (S3), a portion ofthe output side transfer member (102) of the second speed reductiontransfer clutch (C-1) forms the clutch drum (22) of the hydraulic servo(20) of the second speed reduction transfer clutch (C-1), whichhydraulic servo, in turn, is disposed around the boss (3 b).

The above design allows supply of the working oil to the hydraulic servoof the second speed reduction transfer clutch from an oil duct that isprovided in a boss. Thus, in comparison to a structure in which, forexample, the hydraulic servo of the second speed reduction transferclutch is separated from the boss and the working oil is supplied via anoil duct in the input shaft, it is possible to shorten the length of theoil duct by an amount equivalent to the length of the oil duct in theinput shaft, and it is possible to improve the controllability of theautomatic transmission.

An embodiment as shown, for example, in FIGS. 16 through 19 is providedwith a counter gear (15) that is linked to the fourth rotary element(R3) of the planetary gear unit (PU). The counter gear (15) is disposedon the side of the planetary gear unit (PU) axially opposite the speedreduction planetary gear set (DP). The second brake (B-2) is amulti-plate brake that has a plurality of friction plates (71) and isdisposed radially outward of the planetary gear unit (PU).

In comparison to a structure in which, for example, the counter gear islocated between the planetary gear unit and the speed reductionplanetary gear set, the above-described arrangement makes it possible tolink the counter gear to the third rotary element by utilizing, as alocking force transfer member of the second brake, the output sidetransfer member of the second input transfer clutch. In comparison to astructure in which a band brake is located around the output sidetransfer member of the second input transfer clutch, it is possible tolocate the multi-plate brake around the outer circumference of theplanetary gear unit, to reduce size, and to utilize a multiple-platebrake.

An embodiment as shown, for example, in FIGS. 5 through 8, FIGS. 12through 15 has a counter gear (15) that is linked to the fourth rotaryelement (R3) and is axially positioned between the planetary gear unit(PU) and the speed reduction planetary gear set (DP).

A support member (120 a) extending radially inward from the wall (120)of the case (4) supports the counter gear (15). The input side transfermember (112) of the second input transfer clutch (C-2) axially extendsradially outward of the first and second speed reduction transferclutches (C-3, C-1) to where it links with the first speed reductiontransfer clutch (C-3). A portion of the output side transfer member(103) of the second input transfer clutch (C-2) forms the clutch drum(32) of the hydraulic servo (30) of the second input transfer clutch(C-2), which hydraulic servo (30) is disposed around the support member(120 a) and axially intermediate the speed reduction planetary gear set(DP) and the counter gear (15).

In this latter type embodiment, it is possible to supply the working oilto the hydraulic servo of the second input transfer clutch from an oilduct that is provided in the support member. Thus, in comparison to astructure in which, for example, the working oil is supplied from an oilduct in the input shaft, it is possible to reduce the number of sealrings, to reduce the sliding resistance of the seal rings, and toimprove the power transfer efficiency of the automatic transmission.

In an embodiment as shown, for example, in FIG. 7, FIG. 8, FIG. 14, andFIG. 15 a boss (3 b) that extends from the side wall (3 a) of the case(4) supports the stationary element (S1). The input side transfer member(42) of the first speed reduction transfer clutch (C-3) is linked to thespeed reduction rotary element (R1). A portion of the input sidetransfer member (42) of the first speed reduction transfer clutch (C-3)forms the clutch drum (42) of the hydraulic servo (40) of the firstspeed reduction transfer clutch (C-3), and the hydraulic servo (40) isarranged around the boss (3 b) and is positioned axially between thespeed reduction planetary gear set (DP) and the side wall of the case.The input side transfer member (22) of the second speed reductiontransfer clutch (C-1) is linked to the input side transfer member (42)of the first speed reduction transfer clutch (C-3) and a portion of theinput side transfer member (22) of the second speed reduction transferclutch (C-1) forms the clutch drum (22) of the hydraulic servo (20) ofthe second speed reduction transfer clutch (C-1), which hydraulic servo(20) is disposed on support member (120 a) and is axially positionedbetween the speed reduction planetary gear set (DP) and the hydraulicservo (30) of the second input transfer clutch (C-2).

Accordingly, in the above embodiment also, it is possible to supply theworking oil to the hydraulic servo of the first speed reduction transferclutch from an oil duct in the boss extending to the side wall of thecase. Thus, in comparison to a structure in which, for example, thehydraulic servo of the first speed reduction transfer clutch is disposedaround the input shaft, separated from the boss, with the working oilsupplied via an oil duct in the input shaft, it is possible to shortenthe length of the oil duct by an amount equivalent to the length of theoil duct in the input shaft, and to thereby improve the controllabilityof the automatic transmission. In addition, it is possible to supply theworking oil to the hydraulic servo of the second speed reductiontransfer clutch from an oil duct that extends through a wall of the caseand a support wall extending from the case wall. Thus, as compared, forexample, with prior art wherein the working oil is supplied from an oilduct in the input shaft, it is possible to reduce the number of sealrings, to reduce the sliding resistance of the seal rings, and toimprove the power transfer efficiency of the automatic transmission.

In an embodiment shown, for example, in FIG. 6 and FIG. 13, the outputside transfer member (102) of the second speed reduction transfer clutch(C-1) is linked to the second rotary element (S3), a portion of theoutput side transfer member (102) of the second speed reduction transferclutch (C-1) forms the clutch drum (22) of the hydraulic servo (20) ofthe second speed reduction transfer clutch (C-1), and the hydraulicservo (20) is disposed around the support member (120 a) and axiallypositioned between the speed reduction planetary gear set (DP) and thehydraulic servo (30) of the second speed reduction transfer clutch(C-2).

The output side transfer member (101) of the first speed reductiontransfer clutch (C-3) is linked to the first rotary element (S2). Aportion of an output side transfer member (101) of the first speedreduction transfer clutch (C-3) forms the clutch drum (42) of itshydraulic servo (40) which is axially positioned between the speedreduction planetary gear set (DP) and the hydraulic servo (20) of thesecond speed reduction transfer clutch (C-1).

Thus, in the latter type embodiment, it is also possible to supply theworking oil to the hydraulic servo of the second speed reductiontransfer clutch from an oil duct that is provided in a wall that extendsfrom the case and through the support member. In addition, because thehydraulic servo of the first speed reduction transfer clutch is axiallypositioned between the planetary gear unit and the speed reductionplanetary gear set, in comparison to a structure in which, for example,the hydraulic servo of the first speed reduction transfer clutch isdisposed on the side of the speed reduction planetary gear set that isaxially opposite the planetary gear unit, it is possible to shorten thedistance between the first speed reduction transfer clutch and theplanetary gear unit and to shorten the output side transfer member ofthe first speed reduction transfer clutch, which must be strong in orderto transfer a high torque. It is thereby possible to reduce the weight,and to improve the controllability of the automatic transmission.

In addition, the present invention (refer, for example, to FIG. 1through FIG. 19) is provided with a second shaft (81) that is disposedparallel to the input shaft (12) and is linked via the counter gear (15)which is linked to the fourth rotary element (R3). The output rotationfrom the fourth rotary element (R3) is transferred to the second shaft(81) via the counter gear (15).

With the above design the automatic transmission may be advantageouslyused in an FF-type vehicle.

In addition, in the present invention (refer, for example, to FIG. 1through FIG. 15), the counter gear (15) is disposed axially between theplanetary gear unit (PU) and the speed reduction planetary gear set (DP)and is supported by a support member (120 a) that extends from wall(120) of the case (4).

Thereby, it is possible to position the counter gear axially closer tothe input side. Thus, it is possible, for example, to position thesecond shaft and the like closer to the input side (the torque converterside), and thereby make the automatic transmission more compact. As aresult, it is also possible to prevent interference, for example,between the automatic transmission and the frame of the vehicle, wherebymounting of the automatic transmission is facilitated.

In addition, in the present invention (refer, for example, to FIG. 16through FIG. 19), the counter gear (15) is disposed on the side of theplanetary gear unit (PU) axially opposite the speed reduction planetarygear set (DP), and is supported by the support member (120 a).

Thus, it is possible to shorten the distance between the speed reductionplanetary gear set (DP) and the planetary gear unit (PU), and therebyshorten the output side member of the first and second speed reductiontransfer clutches, which must be particularly strong in order totransfer a high torque. Thus, it is possible to reduce the weight andimprove the controllability of the automatic transmission.

In addition, in the present invention (refer, for example, to FIG. 1through FIG. 19), the input side transfer member (CR1) is linked to theinput shaft (12) on the planetary gear unit (PU) side of the speedreduction planetary gear set (DP), and (CR1) is also linked to the inputside transfer member (32 and 112) of the second input transfer clutch(C-2) on the side of the speed reduction planetary gear set (DP) axiallyopposite the planetary gear unit (PU).

Thus, it is possible to link the input rotary element and the input sidetransfer member of the second input transfer clutch with the input shaftwithout a complicated design, and to make the automatic transmissionmore compact.

In addition, in the present invention (refer, for example, to FIG. 1through FIG. 19), the force transfer members (116, 104) of the firstbrake (B-1) are connected to the first rotary element (S2) on the sideof the planetary gear unit (PU) axially opposite the speed reductionplanetary gear set (DP).

Thus, it is possible to simplify the linkage of locking force transfermember of the first brake to the first rotary element and to make theautomatic transmission more compact.

In addition, in the present invention (refer, for example, to FIG. 1through FIG. 9), the stationary element of the speed reduction planetarygear set (DP) includes a first sun gear (S1) and the input rotaryelement of the speed reduction planetary gear set (DP) includes a firstcarrier (CR1) that rotatably supports a first pinion gear (P1) in meshwith the first sun gear (S1) and a second pinion gear in mesh with thefirst pinion gear (P1), and is linked to the input shaft (12). Thereduced speed rotary element of the speed reduction planetary gear set(DP) includes a first ring gear (R1) which meshes with the second piniongear (P2) and which outputs the reduced speed rotation.

Thereby, it is possible to output rotation at a reduced speed, relativeto that of the input shaft, from the first ring gear.

The planetary gear unit (PU) may be a Ravigneaux-type planetary gear setthat includes a second sun gear (S2), a third sun gear (S3), a thirdpinion gear (P3) that meshes with the third sun gear (S3), a fourthpinion gear (P4) that meshes with the second sun gear (S2) and mesheswith the third pinion gear (P3), a second carrier (CR2) that rotatablysupports the third pinion gear (P3) and the fourth pinion gear (P4), anda second ring gear (R3) that meshes with the fourth pinion gear (P4),further comprising:

the first rotary element includes the second sun gear (S2);

the second rotary element includes the third sun gear (S3);

the third rotary element includes the second carrier (CR2); and

the fourth rotary element includes the second ring gear (R3).

Thereby, is it possible to reduce the rotational speeds of each of therotary elements and to obtain advantageous gear ratios while providingsimplified linkages between the rotary elements of the planetary gearunit and the output side members of the clutches.

In the present invention, a first forward speed is established byengaging the second speed reduction transfer clutch (C-1) and lockingthe second brake (B-2). Second forward speed is established by engagingthe second speed reduction transfer clutch (C-1) and locking the firstbrake (B-1). Third forward speed is established by engaging the secondspeed reduction transfer clutch (C-1) and the first speed reductiontransfer clutch (C-3). Fourth forward speed is established by engagingthe second speed reduction transfer clutch (C-1) and the first inputtransfer clutch (C-4). Fifth forward speed is established by engagingthe second speed reduction transfer clutch (C-1) and the second inputtransfer clutch (C-2). Sixth forward speed is established by engagingthe second input transfer clutch (C-2) and the first input transferclutch (C-4). Seventh forward speed is established by engaging thesecond input transfer clutch (C-2) and the first speed reductiontransfer clutch (C-3). Eighth forward speed is established by engagingthe second input transfer clutch (C-2) and locking the first brake(B-1). Reverse speeds are established by engaging the first speedreduction transfer clutch (C-3) or the first input transfer clutch(C-4), and locking the second brake (B-2).

Thus, the automatic transmission of the present invention can establisheight forward speeds in addition to reverse speeds.

Further, in the present invention (refer, for example, to FIG. 14), therotational speed relationships are based on the gear relationships ofthe first, second, third, and fourth rotary elements (S2, S3, CR3, andR3), and in a velocity diagram in which the respective speeds of thefirst, second, third, and fourth rotary elements (S2, S3, CR3, R3) ofthe planetary gear unit (PU) are shown on the ordinate, and thecorresponding gear ratios of the first, second, third, and fourth rotaryelements (S2, S3, CR3, R3) are shown in the abscissa, the first rotaryelement (S2) is positioned to the farthest left side and the thirdrotary element (CR2), the fourth rotary element (R3), and the secondrotary element (S3) are arranged in sequence to the right thereof.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a cross-sectional view of the automatic transmission 1 ₁according to a first embodiment.

FIG. 2 is a skeletal view of the automatic transmission 1 ₁.

FIG. 3 is a table of operations of the clutches and brakes in theautomatic transmission 1 ₁.

FIG. 4 is a velocity diagram for the automatic transmission 1 ₁.

FIG. 5 is a cross-sectional view of an automatic transmission 1 ₂according to a second embodiment.

FIG. 6 is a cross-sectional view of an automatic transmission 1 ₃according to a third embodiment.

FIG. 7 is an enlarged cross-sectional view of an automatic transmission1 ₄ according to a fourth embodiment.

FIG. 8 is a cross-sectional view of an automatic transmission 1 ₅according to a fifth embodiment.

FIG. 9 is a skeletal view drawing of an automatic transmission 1 ₅according to a fifth embodiment.

FIG. 10 is table of operations of the automatic transmission 1 ₅according to a fifth embodiment.

FIG. 11 is a cross-sectional view of an automatic transmission 1 ₆according to a sixth embodiment.

FIG. 12 is a cross-sectional view of an automatic transmission 1 ₇according to a seventh embodiment.

FIG. 13 is a cross-sectional view of an automatic transmission 1 ₈according to an eighth embodiment.

FIG. 14 is a cross-sectional view of an automatic transmission 1 ₉according to a ninth embodiment.

FIG. 15 is a cross-sectional view of an automatic transmission 1 ₁₀according to a tenth embodiment.

FIG. 16 is a cross-sectional view of an automatic transmission 1 ₁₁according to an eleventh embodiment.

FIG. 17 is a cross-sectional view of an automatic transmission 1 ₁₂according to a twelfth embodiment.

FIG. 18 is a cross-sectional view of an automatic transmission 1 ₁₃according to a thirteenth embodiment.

FIG. 19 is a cross-sectional view of an automatic transmission 1 ₁₄according to a fourteenth embodiment.

BEST MODES FOR CARRYING OUT THE INVENTION First Embodiment

Below, a first embodiment of the present invention will be explainedwith reference to FIG. 1 to FIG. 4.

In the following explanation, up, down, left, and right in FIG. 1 andFIG. 2 correspond in sequence to “up”, “down”, “left”, and “right” in anactual automatic transmission 1. In addition, the back portion of theinput shaft 12 and the front portion of the intermediate shaft 13 arespline engaged so that the input shaft 12 and the intermediate shaft 13integrally form an input shaft in a broad sense. The input shaft 12 andthe intermediate shaft 13 will be described in detail below. Inaddition, the direction lengthwise of the input shaft is referred to as“axial” and the direction perpendicular to this axial direction isreferred to as the “radial direction”. Furthermore, for positions in theradial direction, the side near the shaft is referred to as the radiallyinner side (“inner circumferential side”) and the side toward the outerperiphery is referred to as the “radially outer side” (the “outercircumferential side”). Furthermore, in the rotation transfer path fromthe input shaft to the counter gear, for each clutch, the member on theinput shaft side (that is, upstream in the transfer path) of thefriction plates is referred to an “input side transfer member” of theclutch, and the member on the counter gear side (that is, downstream inthe transfer path) is referred to as an “output side transfer member”.

First, the structure of the automatic transmission 1 ₁, as mounted, inan FF-type (front drive, front engine) vehicle, will be explained withreference to FIG. 2. As shown in FIG. 1 and FIG. 2, the automatictransmission 1 ₁ includes a transmission case 3 connected to a case 4that encloses a torque converter 7. The transmission case 3, as shown inFIG. 2, houses a speed change mechanism 2, a counter shaft portion 80,and a differential portion 90. The speed change mechanism 2 is, forexample, on a central axis defined by the input shaft 12 of the speedchange mechanism and the intermediate shaft 13 of the speed changemechanism, which are axially aligned with the shaft 111 of the automatictransmission 1 ₁ that is connected to the output shaft of the engine.The counter shaft 81 of the counter shaft portion 80 is disposed on anaxis that is parallel to the central axis defined by the shaft 12 andthe intermediate shaft 13, and differential portion 90 has left andright vehicle axles 93 l and 93 r aligned on an axis that is parallel tothe counter shaft 81. The input axis 12, the intermediate axis 13, thecounter shaft 81, and the left and right vehicle axles 93 l and 93 rhave a helical positional relationship when viewed from the end side.

Note that for an automatic transmission mounted in an FF-type vehicle,which will be explained below, the left-right direction in the figuresis also the actual left-right direction in the vehicle, and depending onthe direction in which the automatic transmission 1 ₁ is mounted, theright side of the figure may actually be the left side of the vehicleand the left side in the figure may actually be the right side of thevehicle, but in the following description, “right side” and “left side”simply refer to the “right side” and the “left side” in the figures.

As shown in FIG. 2, the torque converter 7 includes a pump impeller 7 athat is connected to the input shaft 11 of the automatic transmission 1₁ and a turbine runner 7 a to which the rotation of the pump impeller 7a is transferred via a working liquid. A turbine runner 7 b is connectedto an input shaft 12 of the speed change mechanism 2, which is axiallyaligned with the input shaft 11. The torque converter 7 is provided witha lock up clutch 10 and, when the lock up clutch 10 is engaged undercontrol of a hydraulic control apparatus (not illustrated), the rotationof the input shaft 11 of the automatic transmission 1 ₁ is directlytransferred to the input shaft 12 of the speed change mechanism 2.

The speed change mechanism 2 is provided with a planetary gear set(speed reduction planetary gear set) DP and a planetary gear unit PUarranged around the input shaft 12 (and the intermediate shaft 13). Theplanetary gear set DP includes a sun gear (“stationary element”; or“first sun gear”) S1, a carrier (input rotary element; first carrier)CR1, and a ring gear (“reduced speed rotary element”; or “first ringgear”) R1, and the carrier CR1 supporting a pinion (“first pinion gear”)P1 that meshes with the sun gear S1 and a pinion (“second pinion gear”)P2 that meshes with the ring gear R1. The pinions P1 and P2 are also inmesh with each other in what is commonly termed a “double pinionplanetary gear set”.

The planetary gear unit PU includes the following four rotary elements:a sun gear S2 (first rotary element; second sun gear); a sun gear S3(second rotary element; third sun gear); a carrier CR2 (CR3) (thirdrotary element; second carrier); and a ring gear R3 (R2) (fourth rotaryelement; second ring gear). The carrier CR2 supports a long pinion(fourth pinion gear) P4 that meshes with the sun gear S2 and the ringgear R3 and a short pinion (third pinion gear) P3 that meshes with a sungear S3 and with long pinion P4 to form what is termed a Ravigneaux-typeplanetary gear set.

The sun gear S1 of the planetary gear set DP is connected to thetransmission case 3 (in a wider sense, the case 4) and thereby heldagainst rotation. The carrier CR1 is connected to the input shaft 12 androtates integrally with the input shaft 12 (hereinafter referred to asthe “input rotation”), and at the same time, is connected to the secondclutch C-2 (the second input transfer clutch). The ring gear R1 rotatesat a speed reduced by the stationary sun gear S1 and the carrier CR1,and is connected to the first clutch C-1 (the “second speed reductiontransfer clutch”) and a third clutch C-3 (the “first speed reductiontransfer clutch”).

The sun gear S2 of the planetary gear unit PU is locked by engagement ofthe first brake B-1 to the transmission case 3. Further, the sun gear S2is connected to a fourth clutch C-4 (“first input transfer clutch”) andthe third clutch C-3, to which the rotation of the input shaft 12 isinput, via the intermediate shaft 13. The rotation of the input shaft 12is selectively input via the fourth clutch C-4 and the reduced speedrotation of the ring gear R1 is selectively input via the third clutchC-3. The sun gear S3, by engagement of the first clutch C-1, receivesthe reduced speed rotation of the ring gear R1.

The carrier CR2 receives the input rotation via the second clutch C-2.In addition, the carrier CR2 is connected to the second brake B-2, andthe rotation is selectively locked (held against rotation) by the secondbrake B-2. In addition, the ring gear R3 is connected to the countergear 15 whereby they rotate in unison.

The large diameter gear 82, which meshes with the counter gear 15, isdisposed on the left end of the counter shaft 81 and a small diametergear 83 is disposed on the right end. A differential ring gear 92 of thedifferential gear apparatus 91 meshes with the small diameter gear 83.Thus, the rotation of the counter gear 15 is transferred to thedifferential ring gear 92 of the differential gear apparatus 91 via thelarge diameter gear 82, the counter shaft 81, and the small diametergear 83. The rotation of the differential ring gear 92 is transferred tothe right and left vehicle axles 93 l and 93 r, while a difference inthe rotational speeds of the right and left vehicle axles 93 l and 93 ris permitted by the differential gear apparatus 91.

The operation of the speed change mechanism 2 described above will nowbe explained with reference to FIG. 2, FIG. 3, and FIG. 4. Note that inthe velocity diagram shown in FIG. 4, the ordinate represents the speedof the respective rotary elements (each gear) and the abscissarepresents the corresponding gear ratios of these rotary elements. Inaddition, in the portion of the velocity diagram for the planetary gearset DP, the ordinate at the left side in FIG. 4 corresponds to the sungear S1 and, the other elements on the ordinate, in sequence toward theright in the figure, represent the ring gear R1 and the carrier CR1.Furthermore, in the portion of the velocity diagram for the planetarygear unit PU, the ordinate to the farthest right side in FIG. 4corresponds to the sun gear S3, and the other elements on the ordinate,in sequence toward the left side in the figure correspond to the ringgear R3 (R2), the carrier CR2 (CR3), and the sun gear S2, respectively.

For example, in the D (drive) range, in the first forward speed (1st),as shown in FIG. 3, the first clutch C-1 and the second brake B-2 areengaged. Thus, as shown in FIG. 2 and FIG. 4, the rotation of the ringgear R1, which receives the reduced speed rotation of the sun gear S1,which is stationary, and the carrier CR1, which provides the inputrotation, is input to the sun gear S3 via the first clutch C-1. Thecarrier CR2 is held against rotation by engagement of the second brakeB-2. Thereby, the reduced speed rotation input to the sun gear S3 isoutput to the ring gear R3 via the stationary carrier CR2, and from thering gear R3 to the counter gear 15 as the first forward speed.

In the second forward speed (2nd), as shown in FIG. 3, the first clutchC-1 is engaged and the first brake B-1 is locked. Thus, as shown in FIG.2 and FIG. 4, the rotation of the ring carrier R1, at a speed as reducedby the stationary sun gear S1, and the carrier CR1 (which provides theinput rotation), is input to the sun gear S3 via the first clutch C-1.The sun gear S2 is held stationary (without rotation) by the locking ofthe first brake B-1, whereby, the carrier CR2 rotates at a speed that isslower than that of the sun gear S3. The reduced speed rotation that isinput to the sun gear S3 is then output to the ring gear R3 via thecarrier CR2, and the rotation of ring gear 3 is output from the countergear 15 as the second forward speed.

In the third forward gear (3rd), as shown in FIG. 3, the first clutchC-1 and the third clutch C-3 are engaged. Thus, as shown in FIG. 2 andFIG. 4, the reduced speed rotation of the ring gear R1 is transferred tothe sun gear S3 via the first clutch C-1. In addition, the reduced speedrotation of the ring gear R1 may be input to the sun gear S2 byengagement of the third clutch C-3. Because the reduced speed rotationof the ring gear R1 is input to the sun gear S2 and the sun gear S3, theplanetary gear unit PU becomes directly linked, the reduced speedrotation is output directly to the ring gear R3, and is output from thecounter gear 15 as the third forward speed.

In the fourth forward speed (4th), as shown in FIG. 3, the first clutchC-1 and the fourth clutch C-4 are engaged. Thus, as shown in FIG. 2 andFIG. 4, the reduced speed rotation of the ring gear R1 is input to thesun gear S3 via the first clutch C-1. The input rotation of the carrierCR1 is input to the sun gear S2 by engagement with the fourth clutchC-4. Thus, the carrier CR2 acquires a reduced speed rotation that is ahigher speed than that of the sun gear S3, the reduced speed rotationreceived by the sun gear S3 is then output to the ring gear R3 via thecarrier CR2, and from the ring gear R3 to the counter gear 15 where itis output as the fourth forward speed.

In the fifth forward speed (5th), as shown in FIG. 3, the first clutchC-1 and the second clutch C-2 are engaged. Thus, as shown in FIG. 2 andFIG. 4, the reduced speed rotation of the ring gear R1 is input to thesun gear S3 via the first clutch C-1. In addition, the input rotation isinput to the carrier CR2 by engagement of the second clutch C-2. Thus, areduced speed rotation, which is at a higher speed than that of thefourth forward speed described above, is output into the ring gear R3.Thus, due to the reduced speed rotation of the sun gear S3 and the inputrotation input to the carrier CR2, the output from the counter gear 15is the fifth forward speed.

In the sixth forward speed (6th), as shown in FIG. 3, the second clutchC-2 and the fourth clutch C-4 are engaged. Thus, as shown in FIG. 2 andFIG. 4, the input rotation of the carrier CR1 is input to the sun gearS2 by engagement of the fourth clutch C-4. In addition, the inputrotation is input to the carrier CR2 by engagement of the second clutchC-2. That is, because the input rotation is input to the sun gear S2 andto the carrier CR2, the planetary gear unit PU is directly coupled, theinput rotation is output directly to the ring gear R3, and the outputfrom the counter gear 15 is the sixth forward speed.

In the seventh forward speed (7th), as shown in FIG. 3, the secondclutch C-2 and the third clutch C-3 are engaged. Thus, as shown in FIG.2 and FIG. 4, the rotation of the ring gear R1 is input to the sun gearS2 via the third clutch C-3. In addition, the input rotation is input tothe carrier CR2 by engagement of the second clutch C-2. Thus, rotationat an increased speed that is slightly higher than that of the inputrotation is output to the ring gear R3, due to the combination ofreduced speed rotation that is input to the sun gear S2 and the inputrotation that is input to the carrier CR2, and the rotation of ring gearR3 is output from the counter gear 15 as the seventh forward speed.

In the eighth forward speed (8th), as shown in FIG. 3, the second clutchC-2 is engaged, and the first brake B-1 is locked. Thus, as shown inFIG. 2 and FIG. 4, the input rotation is received by the carrier CR2 dueto the engagement of the second clutch C-2. In addition, the sun gear S2is held rotationless by the locking of the first brake B-1. Thus, theinput rotation of the carrier CR2 becomes rotation at an increased speedthat is higher than the seventh forward speed and that is output to thering gear R3, and, in turn, is output from the counter gear 15 as theeighth forward speed.

In the first reverse speed (Rev1), as shown in FIG. 3, the third clutchC-3 is engaged, and the second brake B-2 is locked. Thus, as shown inFIG. 2 and FIG. 4, the rotation of the ring gear R1 is input to the sungear S2 via the third clutch C-3. In addition, the carrier CR2 is heldstationary (without rotation) by the locking of the second brake B-2.Thus, the reduced speed rotation that is input to the sun gear S2 isoutput to the ring gear R3 via the carrier CR2, which is stationary, andthe reverse rotation is output from the counter gear 15 as the firstreverse speed.

In the second reverse speed (Rev2), as shown in FIG. 3, the fourthclutch C-4 is engaged, and the second brake B-2 is locked. Thus, asshown in FIG. 2 and FIG. 4, the input rotation of the carrier CR1 due tothe engagement of the clutch C-4 is input to the sun gear S2. Inaddition, the carrier CR2 is held stationary (without rotation) by thelocking of the second brake B-2. Thus, the input rotation that is inputto the sun gear S2 is output to the ring gear R3 via the carrier CR2,which is stationary, and the reverse rotation is output from the countergear 15 as the second reverse speed.

In the P (parking) range and the N (neutral) range, the first clutchC-1, the second clutch C-2, the third clutch C-3, and the fourth clutchC-4 are released. Thereby, the carrier CR1 and the sun gear S2 aredisengaged. In addition, the ring gear R1, the sun gear S2, and the sungear S3 are disengaged and the planetary gear set DP and the planetarygear unit PU are thereby disengaged. Additionally, the input shaft 12(intermediate shaft 13) and the carrier CR2 are disengaged. Therefore,there is no transfer of the driving force from the input shaft 12 to theplanetary gear unit PU, i.e. no transfer of driving force from the inputshaft 12 to the counter gear 15.

Next, the overall configuration of the automatic transmission 1 ₁according to a first embodiment, and in particular, the relativeposition relationships between the essential components, will be brieflyexplained with reference to FIG. 1.

Note that in the following explanation, the words clutch (first throughfourth clutches C-1 to C-4) and brake (first brake B-1, second brakeB-2) are used in a sense that includes both the friction plates (outerfriction plates and inner friction plates) and the hydraulic servos thatengage/disengage them.

As shown in FIG. 1, the automatic transmission 1 ₁ includes a speedchange mechanism 2 ₁ housed within the transmission case 3. Inside thetransmission case 3, the planetary gear unit PU is disposed around theintermediate shaft 13. On the right side (input side) of the planetarygear unit PU, in an axial sequence from the right, are the second clutchC-2, the first clutch C-1, the planetary gear set DP, the third clutchC-3, and the counter gear 15. On the left side of the planetary gearunit PU, disposed in an axial sequence, are the fourth clutch C-4 andthe first brake B-1. The second brake B-2 is located radially outward ofthe planetary gear unit PU.

Within the transmission case 3, to the right of the counter gear 15, insequence from the right end, are the friction plates 31 of the secondclutch C-2, the friction plates 21 of the first clutch C-1, and thefriction plates 41 of the third clutch C-3, all arranged around theinput shaft 12, relatively near the outer wall of the transmission case3.

A partition wall member 3 a that separates the transmission case 3 fromthe housing (case) is attached as a portion of the case 4. The hydraulicservo 30 of second clutch C-2 is mounted on a boss 3 b (the boss 3 b andthe partition wall member 3 a need not be integrally formed) thatextends from partition wall member 3 a. Furthermore, the hydraulic servo20 of the first clutch C-1 is disposed on the left side of the hydraulicservo 30, the planetary gear set DP is disposed radially inward of thefriction plates 21, and the hydraulic servo 40 of the third clutch C-3is disposed substantially radially inward of the friction plates 41.That is, arranged in a sequence from the right side of the transmissioncase 3, are the hydraulic servo 30, the hydraulic servo 20, theplanetary gear set DP, and the hydraulic servo 40 is disposed on theinput shaft 12 adjacent the planetary gear set DP.

A flange-shaped support wall (center support member) 120 extendsradially inward from the inner circumferential surface of thetransmission case 3, on the left side of the hydraulic servo 40 of thethird clutch C-3. Fixed to the radially inner end of the support wall120 is an axially extending sleeve-shaped support member 120 a. Thecounter gear 15, which is connected to the ring gear R3 of the planetarygear unit PU, is rotatable mounted on the support member 120 a via theball bearing assembly 121.

The planetary gear unit PU is disposed on the intermediate shaft 13 onthe left side of the transmission case 3 in the figure, that is, on theleft side of the counter gear 15. The friction plates 71 of the secondbrake B-2 and the hydraulic servo 70 of the second brake B-2 aredisposed radially outward, on the right side of the planetary gear unitPU, and the friction plates 61 of the first brake B-1 are disposedradially outward on the left side of the planetary gear unit PU. Thefriction plates 51 of the fourth clutch C4 are disposed on the left sideof the friction plates 61, and the hydraulic servo 60 of the first brakeB-1 is disposed on the left side of the friction plates 51. Thehydraulic servo 50 of the fourth clutch C-4 located radially inward ofthe hydraulic servo 60.

As explained above, the hydraulic servo 30 of the second clutch C-2 andthe hydraulic servo 20 of the first clutch C-1 are located on the sideof the planetary gear set DP that is axially opposite the planetary gearunit PU, the hydraulic servo 40 of the third clutch C-3 and the countergear 15 are located axially intermediate the planetary gear set DP andthe planetary gear unit PU. The hydraulic servo 50 of the fourth clutchC-4 and the hydraulic servo 60 of the first brake B-1 are disposed onthe side of the planetary gear unit PU that is axially opposite theplanetary gear set DP.

Next, the structure inside the transmission case 3 will be explained indetail with reference to FIG. 1 and the structure of each of the oilducts will be explained together thereafter.

The planetary gear set DP includes a sun gear S1, a carrier CR1, and aring gear R1. The sun gear S1 is mounted on the boss 3 b and therebyfixed so as to be rotationless. The carrier CR1 includes left and rightcarrier plates which rotatably support the pinions P1 and P2therebetween. These pinions P1 and P2 mesh with each other, while theformer pinion P1 also meshes with the sun gear S1 and the latter pinionP2 also meshes with the ring gear R1. The left side carrier plate isconnected to the input shaft 12 and the right side carrier plate isconnected to the clutch drum 32 that is spline engaged with the outerfriction plates among the friction plates 31 of the second clutch C-2.The inner friction plates among the friction plates 21 of the firstclutch C-1 are spline engaged to the outer circumferential surface ofthe ring gear R1. In addition, a hub member 113 is linked to the leftside of the ring gear R1, and the inner friction plates among thefriction plates 41 of the third clutch C-3 are spline engaged to thishub member 113.

The first clutch C-1 is disposed on the boss 3 b via the radially innerportion of the clutch drum 32 of the second clutch C-2, on the rightside of the planetary gear set DP. The first clutch C-1 is provided withfriction plates 21 and a hydraulic servo 20 that engages/disengagesfriction plates 21. This hydraulic servo 20 includes a clutch drum 22, apiston member 23, a cancel plate 24, the oil chamber 26, the cancel oilchamber 27, and a return spring 25, The radially inner portion of theclutch drum 22 is disposed around the outer circumference of theradially inner portion of the clutch drum 32 of the second clutch C-2,and the outer friction plates of the friction plates 21 are splineengaged to the inner circumferential surface of the radially outerportion of the clutch drum 22. The distal end of the radially outerportion of the clutch drum 72 is connected to the transfer member 102,that links to the sun gear S3 of the planetary gear unit PU, through theradially inner side of the counter gear 15. The inner friction platesamong the friction plates 21 are spline engaged to the outercircumferential surface of the ring gear R1 and the hub member 111 thatextends from the ring gear R1. The piston member 23 is axially movablerelative to the clutch drum 22, and an oil-tight oil chamber 26 isformed within the clutch drum 22 by the seal rings a1 and a2. The cancelplate 24 is prevented from moving toward the left by a snap ring 29 thatis fit on the clutch drum 22. A return spring 25 is compressed betweenthe cancel plate 24 and the piston 23 disposed at the right sidethereof, and an oil-tight cancel oil chamber 27 is formed by the sealingrings a1 and a3.

The second clutch C-2 is disposed on the right side of the first clutchC-1 as described above, and radially outward of the boss 3 b. The secondclutch C-2 is provided with friction plates 31 and a hydraulic servo 30engaging/disengaging the friction plates 31. This hydraulic servo 30includes a clutch drum 32, a piston member 33, a cancel plate 34, theoil chamber 36, the cancel oil chamber 37, and a return spring 35. Theleft side end portion of the radially inner portion of the clutch drum32 is linked to the carrier CR1 of the planetary gear set DP. Thehydraulic servo 20 of the first clutch C-1 is disposed around the outercircumference of the left side of the clutch drum 32, and the hydraulicservo 30 is formed on the right side of the clutch drum 32. The outerfriction plates 31 are splined to the inner circumferential surface onthe radially outer portion of the clutch drum 22, and the inner frictionplates 31 are splined to the hub 112. This hub 112 extends around theouter circumference of the first clutch C-1, the planetary gear set DP,and the third clutch C-3 and then extends to the inner circumferentialside of the counter gear 15 where it connects with the transfer member103 that is linked to the right side plate (that is, the planetary gearset DP side) of the carrier CR2 of the planetary gear unit PU. Thepiston member 33 is mounted for axial movement within the clutch drum32, and an oil-tight oil chamber 36 is formed within the clutch drum 32by the seal rings a4 and a5. The cancel plate 34 is limited in itsmovement toward the left by a snap ring 39 that is fit on the clutchdrum 32. A return spring 35 is compressed between the cancel plate 34and the piston member 33 that is disposed on the right side of thecancel plate 34, and an oil-tight cancel oil chamber 37 is formed by theseal rings a4 and a6.

Note that because the clutch drum 32 of this second clutch C-2 isconnected to the input shaft 12 via the carrier CR1, that is, is rotatedwith the same input rotation of the input shaft 12, it is possible tolocate an input rotation speed sensor on the outer circumferential sideof the clutch drum 32. Thus, in comparison to mounting the inputrotation speed sensor so as to directly measure the rotational speed ofthe input shaft 12 mounting of the input rotation speed sensor iseasier.

The third clutch C-3 is on the left side of the planetary gear set DP,around the input shaft 12. The third clutch C-3 is provided withfriction plates 41 and a hydraulic servo 40 that engages/disengagesfriction plates 41. The inner friction plates 41 are spline engaged tothe outer circumferential surface of the hub member 113 that is linkedto the ring gear R1. The outer friction plates 41 are spline engaged tothe inner circumferential surface of the clutch drum 42 which extendsthrough the inner circumferential side of the counter gear 15 andconnects to a transfer member 101 that is linked to the sun gear S2 ofthe planetary gear unit PU.

The hydraulic servo 40 includes a clutch drum 42, a piston member 43, acancel plate 44, forming the oil chamber 46 and the cancel oil chamber47, and a return spring 45. The clutch drum 42 is rotatably mounted onthe left side of the outer circumferential surface of the input shaft12. The piston member 43 is mounted for axial movement within the clutchdrum 42, and an oil-tight oil chamber 46 is formed in the space betweenthe piston member 43 and the clutch drum 42 by the seal rings a7 and a8.A portion of the outer circumferential surface of the piston member 43opposes the friction plates 41. Furthermore, the cancel plate 44 isprevented from moving toward the right by a snap ring 49 that is fittedon the outer circumferential surface of the inner portion of the clutchdrum 42 described above. The return spring 45 is compressed between thecancel plate 44 and the piston member 43, located on the left side ofthe cancel plate 44, and an oil-tight cancel oil chamber 47 is formed bythe seal rings a7 and a9.

The first brake B-1 is located between the outer circumference of theleft portion of the planetary gear unit PU to the side wall portion 3 cof the left side of the transmission case 3. The first brake B-1includes friction plates 61 and a hydraulic servo 60 that engages andreleases friction plates 61. The outer friction plates 61 are splineengaged to the inner circumferential surface of the transmission case 3,and at the same time, the inner friction plates 61 are spline engaged tothe hub member 116 that is linked to the sun gear S2 of the planetarygear unit PU via the transfer member 104.

The hydraulic servo 60 includes a piston member 63, a cancel plate 64,and a return spring 65, and an oil chamber 66 is formed between thepiston member 63 and the transmission case 3. The piston member 63 ismounted for axial movement, and has a right side end portion axiallyaligned in opposition to the friction plates 61. An oil-tight oilchamber 66 is formed in the space between the piston member 63 and thetransmission case 3 by the two seal rings a13 and a14. The cancel plate64 is prevented from moving toward the right side by a snap ring 69 thatis fitted on the inner circumferential surface of the transmission case3.

The second brake B-2 is radially outward of the ring gear R3 of theplanetary gear unit PU and includes friction plates 71 and a hydraulicservo 70 that operates the friction plates 71. The outer friction plates71 are spline engaged with the inner circumferential surface of thetransmission case 3, and the inner friction plates 71 are spline engagedwith the hub member 117 that is linked to the carrier CR2 of theplanetary gear unit PU.

The hydraulic servo 70 includes a cylinder 72, a piston 73, a cancelplate 74, a return spring 75, and an oil chamber 76 formed between thecylinder 72 and the piston 73. The piston 73 is mounted for axialmovement, and has a right side end portion axially aligned in oppositionto the friction plates 71. An oil-tight oil chamber 76 is formed in thespace between the piston 73 and the transmission case 3 by the two sealrings a15 and a16. The cancel plate 74 is prevented from movement towardthe right by a snap ring 79 that is fitted on the inner circumferentialsurface of the transmission case 3.

The fourth clutch C-4 is located to the left of the planetary gear unitPU, radially inward of the first brake B-1, and includes friction plates51 and a hydraulic servo 50 that operates the friction plates 51. Theinner friction plates 51 are linked to the hub member 116 by splineengagement with the hub member 114 that is linked to the carrier CR2 viathe transfer member 104. The outer friction plates 51 are spline engagedwith the inner circumferential surface of the clutch drum 52 and theclutch drum 52 is linked to the intermediate shaft 13. This intermediateshaft 13 is spline engaged with the input shaft 12, that is, the clutchdrum 52 is linked to the input shaft 12 via the intermediate shaft 13.In this manner, the fourth clutch C-4 can directly engage and disengagethe input shaft 12 (intermediate shaft 13) and the sun gear S2, ratherthan through the carrier CR1 of the planetary gear set DP.

The hydraulic servo 50 includes a clutch drum 52, a piston 53, a cancelplate 54, a return spring 55, an oil chamber 56 and a cancel oil chamber57. At its right side end, the clutch drum 52 is connected to theintermediate shaft 13. The clutch drum 52 is supported for free rotationon the boss 3 d extending from the side wall portion 3 a of thetransmission case 3. The piston 53 is mounted for axial movement withinthe clutch drum 52, and an oil-tight oil chamber 56 is formed in thespace between the piston 53 and the clutch drum 52 by seal rings a10 andall. A radially outer portion of the piston member 53 is axially alignedin opposition to the friction plates 51. The cancel plate 54 isprevented from moving toward the right by a snap ring 59 that is fittedon the outer circumferential surface of the inner portion of the clutchdrum 52. A return spring 55 is compressed between the cancel plate 54and the piston member 53 that is disposed on the left side thereof, andan oil-tight cancel oil chamber 57 is formed by the seal rings a10 anda12.

The planetary gear unit PU includes a sun gear S2, a sun gear S3, ashort pinion P3 that meshes with the sun gear S3, a long pinion P4 thatmeshes with the sun gear S2, the short pinion P3, and the ring gear R3,a carrier CR2 that rotatably supports the short pinion P3 and the longpinion P4 between two end plates, and a ring gear R3 that meshes withthe long pinion P4, thereby forming a Ravigneaux-type planetary gearset.

The transfer member 101 that passes through the inner circumference ofthe counter gear 15 is linked to the right side of the sun gear S2, andthe sun gear S2 is thereby linked to the clutch drum 42 of the thirdclutch C-3 via the transfer member 101. The transfer member 104described above is linked to the left side of the sun gear S2, and thesun gear S2 is linked to the hub member 114 of the fourth clutch C4 andto the hub member 116 of the first brake B-1 via the transfer member104. The transfer member 102 that passes through the innercircumferential side of the counter gear 15 is linked to the right sideof the sun gear S3, and the clutch drum 22 of the first clutch C-1 islinked to the sun gear S3 via the linking member 102.

The right side of the carrier CR2, that is, the side plate on theplanetary gear set DP side, is linked to the transfer member 103 thatpasses through the inner circumference of the counter gear 15 and isthereby linked to the hub member 112 of the second clutch C-2 via thetransfer member 103. The side plate on the left side of the carrier CR2is linked to the hub member 117 of the second brake B-2. The ring gearR3 is connected to the counter gear 15 via the transfer member 105. Thecounter gear 15 meshes with the large diameter gear 82 that is mountedon the counter shaft 81, and links to the left and right wheels 93 l and93 r (that is, the drive wheels) via the counter shaft 80 and thedifferential gear portion 90.

Next, the structure of each of the oil ducts and the supply of theworking oil will be briefly explained. The oil duct c30 in the boss 3 bcommunicates with the oil chamber 36 of the hydraulic servo 30 of thesecond clutch C-2, that is, the oil chamber 36 that is formed by sealingthe space between the clutch drum 32 and the piston 33 by the seal ringsa4 and a5. Working oil is supplied through the space between the clutchdrum 32 and the boss 3 b and formed between the seal rings d1 and d2,from the oil duct c30. Likewise, oil is supplied from an oil duct (notillustrated) to the cancel oil chamber 37 that is formed by sealing thespace between the piston member 33 and the cancel plate 34 with the sealrings a4 and a6.

In addition, the oil duct c20 in the boss 3 b communicates with the oilchamber 26 of the hydraulic servo 20 of the first clutch C-1, that is,the oil chamber 26 that is formed by sealing the space between theclutch drum 22 and the piston 23 by the seal rings a1 and a2, throughthe space between the clutch drum 32 of the second clutch C-2 and theboss 3 b sealed between the seal rings d3 and d4, and through the spacebetween the seal rings d5 and d6, whereby, working oil is supplied fromthe oil duct c20. Likewise, oil is supplied from an oil duct (notillustrated) to the cancel oil chamber 27 that is formed by sealing thespace between the piston 23 and the cancel plate 24 with the seal ringsa1 and a3.

The oil duct c40 in the boss 3 b communicates via the oil ducts c41,c42, and c43 in the input shaft 12, with the oil chamber 46 of thehydraulic servo 40 of the third clutch C-3, that is, the oil chamber 46formed by sealing the space between the clutch drum 42 and the pistonmember 43 with the seal rings a7 and a8. This supply of oil also passesthrough the space between the boss 3 b and the input shaft 12 sealedbetween the seal rings d7 and d8, and through the space between theinput shaft 12 and the clutch drum 42 between the seal rings d9 and d10.Likewise, oil is supplied from an oil duct (not illustrated) to thecancel oil chamber 47 that is formed by sealing the space between thepiston 43 and the cancel plate 44 by the seal rings a7 and a9.

The oil duct c50 in the boss 3 d communicates with the oil chamber 56 ofthe hydraulic servo 50 of the fourth clutch C-4, that is, the oilchamber 56 formed by sealing the space between the clutch drum 52 andthe piston member 53 with the sealing rings a10 and a11, and through thespace between the clutch drum 52 and the boss 3 d defined between theseal rings d11 and d12. Likewise, oil is supplied from an oil duct (notillustrated) to the cancel oil chamber 57 that is formed by sealing thespace between the piston member 53 and the cancel plate 54 with the sealrings a10 and a12.

In addition, working oil is supplied from an oil duct (not illustrated)in the side wall portion 3 c to the oil chamber 66 of the hydraulicservo 60 of the first brake B-1, that is, the oil chamber 66 that isformed by sealing the space between the side wall portion 3 c of thetransmission case 3 and the piston 63 with the seal rings a13 and a14.

Working oil is also supplied from an oil duct (not illustrated) in thetransmission case 3 to the oil chamber 76 of the hydraulic servo 70 ofthe second brake B-2, that is, the oil chamber 76 that is formed bysealing the space between the cylinder member 72 and the piston 73 withthe seal rings a15 and a16.

In addition, an oil duct c80 extends axially through the input shaft 12and the intermediate shaft 13, and lubricating oil is supplied from anoil duct (not illustrated) in the boss 3 b or the boss 3 d to the oilduct c80. A plurality of holes (not illustrated) are bored in the inputshaft 12 and the intermediate shaft 13 in radial alignment with the oilduct c80, and the lubricating oil that is supplied to the oil duct c80is supplied into the speed change mechanism 2 ₁ as a spray from theseholes.

In addition, an oil duct c90 is axially formed in the input shaft 12 andcommunicates with the lock up clutch 10 via an oil duct (notillustrated). Thus, when working oil is supplied to the oil duct c90from a hydraulic control apparatus (not illustrated) via an oil duct inthe boss 3 b, the friction plates of the lock up clutch 10 are pressedtogether, and the lock up clutch 10 is thereby engaged.

In contrast, in the automatic transmission that is shown in FIG. 19 ofJapanese Patent Application Publication No. JP-A-2004-183705, an inputrotary element of a speed reduction planetary gear set and a rotaryelement of a second planetary gear set are adapted to be selectivelylocked by clutches, but assuming that the transfer member that transfersthis input rotation is linked to the rotary element of the secondplanetary gear set, extends along the outer circumference of the secondplanetary gear set and radially inward to link with the input rotaryelement of the speed reduction planetary gear set, the transfer memberlinked to the rotary element encloses the second planetary gear set.

However, disposition of the transfer member on the outer circumferenceside of the second planetary gear set in this manner hinders making theautomatic transmission more radially compact. In addition, because thetransfer member is disposed on the radially outermost side, thecentrifugal force generated during rotation requires a high rigidity, athicker transfer member, and added weight, thus increasing inertia andhindering controllability.

In addition, in the above-described prior art transmission, because eachof the rotary elements of the second planetary gear set rotate relativeto each other, lubricating oil must be supplied and cooled, but thatsupply (and discharge) is hindered by the transfer member which enclosesthe planetary gear set, and heat is easily accumulated; that is, it isnot possible to ensure cooling performance. Furthermore, when, forexample, sufficient holes are provided in the transfer member so thatthe lubricating oil can be discharged smoothly, there are problems inthat it is necessary to make the transfer member even thicker in orderto provide the necessary high rigidity, and the weight is furtherincreased.

In addition, because the above-described prior art transfer memberencloses a section from the speed reduction planetary gear set to thesecond planetary gear set, the assembly of the automatic transmission isdifficult. Furthermore, even if, for example, the transfer member wereto be partitioned into a plurality of sections and linked by splines orthe like, such splines would require positioning, making the assembly ofthe automatic transmission more difficult.

In addition, because the prior art transfer member also encloses otherclutches, for example, it is not possible to provide a structureincluding a center support member, supply of working oil for a clutchthrough a center support member is precluded. Further, because it isnecessary to supply the working oil to such a clutch hydraulic servofrom the input shaft (in particular, via members that rotate relative toeach other), there are problems in that the number of seal rings must beincreased and the sliding resistance increased, hindering the powertransfer efficiency.

In contrast, in the automatic transmission 1 ₁ of the present invention,there is no member enclosing the planetary gear unit PU because thefourth clutch C-4 is interposed in the transfer path between input shaft12 and the sun gear S2, the second clutch C-2 interposed in the transferpath between the carrier CR1 and the carrier CR2, and the output sidetransfer member 103 of the second clutch C-2 is linked to the carrierCR2 in the planetary gear unit PU at the axial side of the planetarygear set DP. It is thereby possible to make the automatic transmission 1₁ more axially compact. In addition, it is possible to shorten thetransfer member that requires a high rigidity, and thereby improve thecontrollability of the automatic transmission 1 ₁. Further, the presentinvention provides a simplified structure in which the supply oflubricating oil is readily discharged, thereby ensuring coolingperformance. Furthermore, the arrangement of the clutches enables astructure including a support wall 120 through which working oil of aclutch is supplied. Thus, it is possible to reduce the number of sealrings, to reduce the sliding resistance of the seal rings, and toimprove the power transfer efficiency of the automatic transmission 1 ₁.

In addition, because the counter gear 15 that is linked to the ring gearR3 is disposed axially intermediate the planetary gear unit PU and theplanetary gear set DP, and the output side member 101 of the thirdclutch C-3, the output side transfer member 102 of the first clutch C-1,and the output side transfer member 103 of the second clutch C-2 connectwith the planetary gear unit PU through the radially inner side of thecounter gear 15, it is possible to dispose the counter gear 15 axiallyintermediate the planetary gear unit PU and the planetary gear set DP,and it is possible to advantageously use the automatic transmission 1 ₁in an FF-type vehicle.

Furthermore, because the hydraulic servo 30 of the second clutch C-2 isdisposed on the side of the planetary gear set DP that is axiallyopposite the planetary gear unit PU, it is possible to supply workingoil from an oil duct c30 in the boss 3 b to the hydraulic servo 30 ofthe second clutch C-2. It is thereby possible to reduce the number ofseal rings as compared to a structure in which the working oil issupplied from an oil duct in the input shaft 12. It is thereby possibleto reduce the sliding resistance of the seal rings, and to improve thepower transfer efficiency of the automatic transmission 1 ₁.

In addition, because the hydraulic servo 50 of the fourth clutch C-4 isdisposed on the side of the planetary gear unit PU axially opposite theplanetary gear set DP, it is possible to locate the friction plates 51of the fourth clutch C-4 relatively near the outer circumference of thecase and to enlarge the area of the friction plates 51. Thereby, it ispossible to ensure torque capacity while reducing the number of thefriction plates 51. Furthermore, it is possible to supply working oil tothe hydraulic servo 50 of the fourth clutch C-4 from the oil duct c50that is provided inside the boss 3 d. Therefore, the number of sealrings may be reduced in comparison to a structure in which the workingoil is supplied from an oil duct inside the input shaft 12, to reducethe sliding resistance of the seal rings, and to improve the powertransfer efficiency of the automatic transmission 1 ₁.

Furthermore, because the hydraulic servo 40 of the third clutch C-3 islocated axially intermediate the planetary gear unit PU and theplanetary gear set DP, as compared to a structure which the hydraulicservo 40 of the third clutch C-3 is disposed on the side of theplanetary gear set DP axially opposite the planetary gear unit PU, it ispossible to shorten the distance between the third clutch C-3 and theplanetary gear unit PU, and to shorten the output side transfer member101 of the third clutch C-3, which member requires strength fortransferring a high torque. In this manner, the weight is reduced andthe controllability of the automatic transmission 1 ₁.is improved.

In addition, because the hydraulic servo 20 of the first clutch C-1 islocated on the side of the planetary gear set DP axially opposite theplanetary gear unit PU, it is possible to supply working oil to thehydraulic servo 20 of the first clutch C-1 from the oil duct c20 in theboss 3. Thereby, for example, as compared to a structure in which thehydraulic servo 20 of the first clutch C-1 is disposed on the inputshaft 12 and working oil is supplied via the input shaft 12, it ispossible to shorten the length of the oil duct, and thereby improve thecontrollability as an automatic transmission 1 ₁.

Furthermore, because a first brake B-1 is provided that selectivelylocks the sun gear S2 to the case 4 and the hydraulic servo 60 of thefirst brake B-1 is disposed on the side of the planetary gear unit PUaxially opposite the planetary gear set DP, it is possible to link theoutput side transfer member of the first brake B-1 to the sun gear S2without a complicated configuration, and to make the automatictransmission 1 ₁ more compact.

In the automatic transmission 1 ₁ according to the present invention, asexplained above, the transfer member 103 of the output side of thesecond clutch C-2 is linked to the carrier CR2, extending along theouter circumference of the transfer members 101, 102 of the output sidesof the third and first clutches C-3, C-1, the transfer member 104 of theoutput side of the fourth clutch C-4 and the transfer member 101 of theoutput side of third clutch C-3 are linked to the sun gear S2, and thetransfer member 104 of the output side of the fourth clutch C-4, thetransfer member 101 of the output side of third clutch C-3, and the sungear S2, which rotate integrally therewith, are disposed on the innercircumferential side of the transfer member 102 of the output side ofthe first clutch C-1. Therefore, the transfer member 104 of the outputside of the fourth clutch C4, which rotates faster than the transfermember 103 of the output side of the second clutch C-2, is located moreradially inward than the transfer member 102 of the output side of thefirst clutch C-1, which is on the inner side of the transfer member 103of the output side of the second clutch C-2. As a result, it is possibleto make the diameter of the transfer member 104 of the output side ofthe fourth clutch C-4 smaller than the diameter of the transfer member103 of the output side of the second clutch C-2, and thus it is possibleto reduce the weight more than in a structure in which the transfermember 102 is on the outer side of transfer member 103. In addition,because the inertia is reduced in comparison to a structure in which thetransfer member 102 is located on the outer side, the controllability ofthe automatic transmission 1 ₁ is improved.

The third and first clutches C-3, C-1 are disposed on the side of theplanetary gear set DP relative to the planetary gear set PU, thetransfer members 101, 102 of the output side of the third and firstclutches C-3, C-1 are respectively linked to the sun gear S2 and the sungear S3, the fourth clutch C-4 is located on the side of the planetarygear unit PU axially opposite the planetary gear set DP, the transfermember 104 of the output side of the fourth clutch C-4 is linked to thesun gear S2, the second clutch C-2 is disposed on the planetary gear setDP side relative to the planetary unit PU, and the transfer member 103of the output side of the second clutch C-2 is linked to the carrier CR2extending outward of the outer circumference of the transfer members101, 102 of the output sides of the third and first clutches C-3, C-1.Because the transfer member 104 of the output side of the fourth clutchC-4, which rotates faster than the transfer member of the output side ofthe second clutch C-2, is located more radially inward, the diameter ofthe transfer member 104 of the output side of the fourth clutch C-4 canbe made smaller than the diameter of the transfer member 103 of theoutput side of the second clutch C-2, and it is possible to reduce theweight as compared to a configuration in which the transfer member 104is disposed on the outer circumferential side. In addition, because itis possible to reduce the inertia as compared to a configuration inwhich the transfer member 104 is on the outer side, it is possible toimprove the controllability of the automatic transmission 1 ₁.

In addition, as compared to a structure in which the hydraulic servo 50of the fourth clutch C-4 is located between the planetary gear unit PUand the planetary gear set DP, the friction plates 51 of the fourthclutch C-4 are located more radially outward, and it is possible toincrease the area of the friction plates. Thus, it is possible to ensurean adequate torque transfer capacity while reducing the number offriction plates 51. Furthermore, it is possible to shorten the distancebetween the third and first clutches C-3, C-1 and the planetary gearunit PU, and it is possible to shorten the transfer members 101, 102 ofthe output sides of the third and first clutches C-3, C-1, which must besufficiently strong to transfer a high torque. It is thereby possible todecrease the weight to improve the controllability of the automatictransmission 1 ₁.

Furthermore, it is possible, for example, to supply the working oil tothe hydraulic servo 50 of the fourth clutch C-4 from an oil duct c50provided in the boss 3 b. Thereby, in comparison to a structure in whichthe working oil is supplied from an oil duct in the input shaft 12, itis possible to reduce the number of seal rings, to reduce the slidingresistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₁.

In addition, because the transfer member of the input side of the fourthclutch C-4 is linked to the input shaft 12 and to intermediate shaft 13through the inner side of the planetary gear unit PU and a portion ofthe transfer member of the input side of the fourth clutch C4 forms theclutch drum 52 of the hydraulic servo 50 of the fourth clutch C-4, incomparison to a structure in which the transfer member of the outputside of the fourth clutch C-4 forms the clutch drum of the hydraulicservo 50, the clutch drum of the hydraulic servo 50 can also serve totransfer power from the input shaft 12, and thus it is possible toshorten the transfer member.

Furthermore, because the boss 3 b supports and holds the sun gear S1stationary, because the transfer member of the input side of the secondclutch C-2 is linked to the carrier CR1 and a portion of the transfermember of the input side of the second clutch C-2 forms the clutch drum32 of the hydraulic servo 30 of the second clutch C-2, and because thehydraulic servo 30 is disposed around the boss 3 b axially intermediatethe planetary gear set DP and the side wall 3 a, it is possible tosupply the working oil to the hydraulic servo 30 of the second clutchC-2 from an oil duct c30 in the boss 3 b. Thus, in comparison to astructure in which the hydraulic servo 30 of the second clutch C-2 isdisposed around the input shaft 12, separated from the boss 3 b, and theworking oil is supplied via an oil duct in the input shaft 12, it ispossible to shorten the length of the oil duct by an amount equivalentto the length of the oil duct in the input shaft 12, and it is possibleto improve the controllability of the automatic transmission 1 ₁.

In addition, because: (1) the hub 111 of the first clutch C-1 is linkedto the ring gear R1, (2) the transfer member 102 of the output side ofthe first clutch C-1 is linked to the sun gear S3, (3) a portion of thetransfer member 102 forms the clutch drum 22 of the hydraulic servo 20of the first clutch C-1, and (4) the hydraulic servo 20 is disposedaround the boss 3 b axially intermediate the planetary gear set DP andthe hydraulic servo 20 of the second clutch C-1, it is possible tosupply the working oil to the hydraulic servo 20 of the first clutch C-1from an oil duct c20 in the boss 3 b. Thus, in comparison to a structurein which, for example, the hydraulic servo 20 of the first clutch C-1 isdisposed around the input shaft 12, separated from the boss 3 b and theworking oil is supplied via an oil duct in the input shaft 12, it ispossible to shorten the length of the oil duct by an amount equivalentto the length of the oil duct in the input shaft 12, and to improve thecontrollability of the automatic transmission 1 ₁.

Furthermore, because counter shaft 81 is parallel to the input shaft 12and linked via the counter gear 15 that is linked to the ring gear R3,and the output rotation from the ring gear R3 is transferred to thecounter shaft 81 via the counter gear 15, it is possible toadvantageously use the automatic transmission 1 ₁ for a FF-type vehicle.

Because the counter gear 15 is located axially intermediate theplanetary gear unit PU and the planetary gear set DP and is supported bya support member 120 a extending from the support wall 120, it ispossible to position the counter gear 15 axially further toward theinput side. For example, it is possible to position the counter shaftportion 80 and the differential gear portion 90 near the torqueconverter 7 side, thereby making the automatic transmission 1 ₁ morecompact. Thus, it is possible to avoid interference between thetransmission 1 ₁ and the frame of the vehicle.

Furthermore, because the carrier CR1 is linked to the input shaft 12 onthe side of the planetary gear set DP facing the planetary gear unit PUand has an axially extending linkage to the clutch drum 32, which alsoserves as the transfer member of the input side of the second clutchC-2, at the side of the planetary gear set DP opposite the planetarygear unit PU, it is possible to link the carrier CR1, the transfermember 32 of the input side of the second clutch C-2, and the inputshaft 12 without complicated configuration of the components, and it ispossible to make the automatic transmission 1 ₁ more compact.

In addition, because the hub member 116 of the first brake B-1 and thetransfer member 104 that is linked thereto are axially linked to the sungear S2 at the side of the planetary gear unit PU opposite the planetarygear set DP, it is possible to link together the hub member 116 of thefirst brake B-1, the transfer member 104, and the sun gear S2 without acomplicated configuration of components, and to make the automatictransmission 1 ₁ more compact.

In addition, because the planetary gear set DP includes a sun gear S1which normally does not rotate, a carrier CR1 that rotatably supportsthe pinion gear P1 and the pinion gear P2 and that is coupled to theinput shaft 12, and a ring gear R1 that meshes with the pinion gear P2and outputs a reduced speed rotation, it is possible to output from thering gear R1 a reduced speed rotation, i.e. rotation at a speed lessthan that of the input rotation of the input shaft 12.

In addition, because the planetary gear unit PU is a Ravigneaux-typeplanetary gear unit that includes a sun gear S2, a sun gear S3, a shortpinion P3 that meshes with the sun gear S3, a long pinion P4 that mesheswith the sun gear S2 and with the short pinion P3, a carrier CR2 thatselectively rotatably supports the short pinion P3 and the long pinionP4, and the ring gear R3 that meshes with the long pinion P4, it ispossible to link each of the rotary elements of the planetary gear unitPU and the output side members of each of the clutches and brakeswithout making these members complicated, and at the same time it ispossible to prevent high speed rotation of each of the rotary members,and to obtain favorable gear ratios.

The first forward speed can be established by engaging the first clutchC-1 and locking the second brake B-2; the second forward speed can beestablished by engaging the first clutch C-1 and locking the first brakeB-1; the third forward speed can be established by engaging the firstclutch C-1 and the third clutch C-3; the fourth forward speed can beestablished by engaging the first clutch C-1 and the fourth clutch C-4;the fifth forward speed can be established by engaging the first clutchC-1 and the second clutch C-2; the sixth forward speed can beestablished by engaging the second clutch C-2 and the fourth clutch C-4;the seventh forward speed can be established by engaging the secondclutch C-2 and the third clutch C-3; the eighth forward speed can beestablished by engaging the second clutch C-2 and locking the firstbrake B-1; and reverse speeds can be established by engaging the thirdclutch C-3 or the fourth clutch C-4 and locking the second brake B-2.

In a velocity diagram in which the respective speeds of the sun gear S2,the sun gear S3, the carrier CR2, and the ring gear R3 of the planetarygear unit PU are on the ordinate, and the corresponding gear ratios ofthe sun gear S2, the sun gear S3, the carrier CR2, and the ring gear R3are on the abscissa, a structure becomes possible in which the sun gearS2 is positioned at the farthest left end of the ordinate and, insequence therefrom, are the carrier CR2, the ring gear R3 that is linkedto the counter gear 15, and the sun gear S3.

The automatic transmission 1 ₁ according to the first embodiment becomesan automatic transmission 1 ₆ according to the sixth embodimentdescribed below (FIG. 11) by axially reversing the speed changemechanism 2 ₁, i.e. by reversing the relative axial positions of theplanetary gear sets PU and DP.

Second Embodiment

Next, a second embodiment, in which a portion of the first embodimenthas been modified, will be explained with reference to FIG. 5 which is across-sectional view showing the automatic transmission 1 ₂ of thesecond embodiment. Note that in the second embodiment explained below,only the portions that differ from the automatic transmission 1 ₁ of thefirst embodiment will be explained. The other portions are substantiallyidentical, and explanation thereof will be omitted.

In contrast to the automatic transmission 1 ₁ of the first embodiment,the automatic transmission 1 ₂ of the second embodiment has a structurethat is modified such that the hydraulic servo 30 of the second clutchC-2 is located axially intermediate the planetary gear set DP and theplanetary gear unit PU, and more specifically, the hydraulic servo 30 ofthe second clutch C-2 is located axially intermediate the counter gear15 and the hydraulic servo 40 of the third clutch C-3 and adjacent asupport wall 120.

Specifically, in automatic transmission 1 ₂, the hydraulic servo 20 ofthe first clutch C-1 is disposed on the side of the planetary gear setDP axially opposite the planetary gear unit PU, the hydraulic servo 40of the third clutch C-3, the hydraulic servo 30 of the second clutchC-2, and the counter gear 15 are located axially intermediate theplanetary gear set DP and the planetary gear unit PU, and the hydraulicservo 50 of the fourth clutch C4 and the hydraulic servo 60 of the firstbrake B-1 are disposed on the side of the planetary gear unit PU that isaxially opposite the planetary gear set DP.

In the automatic transmission 1 ₂, because the fourth clutch C-4 islocated in the transfer path to connect the input shaft 12 and the sungear S2, the second clutch C-2 is located in the transfer path so as toconnect the carrier CR1 and the carrier CR2, and the output sidetransfer member 103 of the second clutch C-2 is axially linked to thecarrier CR2 on the side of the planetary gear unit PU facing theplanetary gear set DP, it is possible to avoid need for a memberenclosing the planetary gear unit PU. The automatic transmission 1 ₂ canthereby be made more radially compact. In addition, it is possible toshorten the transfer member, which requires a high rigidity, and tothereby reduce the weight and improve the controllability. Furthermore,the lubricating oil is readily discharged, and the cooling performancecan be ensured. In addition, the assembly of the automatic transmission1 ₂ can be simplified. Furthermore, because of provision of support wall120, the working oil for the clutches can be supplied from this supportwall 120 enabling a reduction in the number of seal rings, a reductionin the sliding resistance of the seal rings, and an improvement thepower transfer efficiency of the automatic transmission 1 ₂.

In addition, because the hydraulic servo 30 of the second clutch C-2 isdisposed axially intermediate the planetary gear unit PU and theplanetary gear set DP, it is possible to supply working oil to thehydraulic servo 30 of the second clutch C-2 from an oil duct provided inthe support wall 120. Thereby, in comparison to a structure in which theworking oil is supplied from an oil duct in the input shaft 12, it ispossible to reduce the number of seal rings, to reduce the slidingresistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₂.

Furthermore, because the hydraulic servo 50 of the fourth clutch C-4 islocated on the side of the planetary gear unit PU that is axiallyopposite the planetary gear set DP, it is possible to locate thefriction plates 51 of the fourth clutch C-4 further radially outward andto make the surface area of the friction plates 51 larger. Therefore, itis possible to ensure transfer of a sufficient torque, while reducingthe number of friction plates. Furthermore, it is possible to supplyworking oil to the hydraulic servo 50 of the fourth clutch C-4 from anoil duct that is provided in the boss 3 d. Thereby, in comparison to astructure in which the working oil is supplied from an oil duct in theinput shaft 12, it is possible to reduce the number of seal rings, toreduce the sliding resistance of the seal rings, and to improve thepower transfer efficiency of the automatic transmission 1 ₂.

In addition, because the hydraulic servo 40 of the third clutch C-3 isdisposed axially intermediate the planetary gear unit PU and theplanetary gear set DP, in comparison to a structure in which thehydraulic servo 40 of the third clutch C-3 is disposed on the side ofthe planetary gear set DP that is axially opposite the planetary gearunit PU, it is possible to shorten the distance between the third clutchC-3 and the planetary gear unit PU and to shorten the output sidetransfer member 101 of the third clutch C-3, which must be strong inorder to transfer high torque. It is thereby possible to reduce theweight and to improve the controllability of the automatic transmission1 ₂.

Furthermore, because the hydraulic servo 20 of the first clutch C-1 isdisposed on the side of the planetary gear set DP that is axiallyopposite the planetary gear unit PU, it is possible to supply workingoil to the hydraulic servo 20 of the first clutch C-1 from an oil ductprovided in the boss 3 b. Thereby, in comparison to a structure in whichworking oil is supplied from an oil duct in the input shaft 12, it ispossible to reduce the number of seal rings, to reduce the slidingresistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₂.

In addition, because of provision of a first brake B-1 that selectivelystops rotation of the sun gear S2 and because the hydraulic servo 60 ofthe first brake B-1 is located on the side of planetary gear unit PUthat is axially opposite the planetary gear set DP, the locking forcetransfer member of the first brake B-1 and the sun gear S2 can be linkedwithout complicating the configuration of these components, and it ispossible to make the automatic transmission 1 ₂ more compact.

In the automatic transmission 1 ₂ according to the present invention, asexplained above, the transfer member 103 of the output side of thesecond clutch C-2 is linked to the carrier CR2 radially outward of thetransfer members 101, 102 of the output side of the third and firstclutches C-3, C-1, the transfer member 104 of the output side of thefourth clutch C-4 and the transfer member 101 of the output side ofthird clutch C-3 are linked to the sun gear S2, and the transfer member104 of the output side of the fourth clutch C4, the transfer member 101of the output side of third clutch C-3, and the sun gear S2, whichrotate integrally therewith, are disposed radially inward of thetransfer member 102 of the output side of the first clutch C-1.Therefore, the transfer member 104 of the output side of the fourthclutch C-4, which rotates faster than the transfer member 103 of theoutput side of the second clutch C-2, is radially inward of the transfermember 102 of the output side of the first clutch C-1, which, in turn,is radially inward of the transfer member 103 of the output side of thesecond clutch C-2. As a result, it is possible to make the diameter ofthe transfer member 104 of the output side of the fourth clutch C4smaller than the diameter of the transfer member 103 of the output sideof the second clutch C-2, and to reduce the weight as compared to theweight when it is on the radially outer side. In addition, because theinertia is reduced in comparison to a structure in which it is disposedon the radially outer side, it is possible to improve thecontrollability of the automatic transmission 1 ₂.

In addition, the third and first clutches C-3, C-1 are disposed on theplanetary gear set DP side of the planetary gear set PU, the transfermembers 101, 102 of the output side of the third and first clutches C-3,C-1 are respectively linked to the sun gear S2 and the sun gear S3, thefourth clutch C-4 is disposed on the side of the planetary gear unit PUthat is axially opposite the planetary gear set DP, the transfer member104 of the output side of the fourth clutch C-4 is linked to the sungear S2, the second clutch C-2 is disposed on the planetary gear set DPside of the planetary unit PU, and the transfer member 103 of the outputside of the second clutch C-2 is linked to the carrier CR2 radiallyoutward of the transfer members 101, 102 of the output side of the thirdand first clutches C-3, C-1. Thereby, because the transfer member 104 ofthe output side of the fourth clutch C-4, which rotates faster than thetransfer member of the output side of the second clutch C-2, is locatedmore radially inward, the diameter of the transfer member 104 of theoutput side of the fourth clutch C-4 can be made smaller than thediameter of the transfer member 103 of the output side of the secondclutch C-2, and it is possible to reduce the weight as compared to thecase in which it is disposed on the radially outer side. In addition,because it is possible to reduce the inertia as compared to anarrangement in which it is further radially outward, it is possible toimprove the controllability of the automatic transmission 1 ₂.

In addition, in comparison to an arrangement wherein the hydraulic servo50 of the fourth clutch C-4 is located between the planetary gear unitPU and the planetary gear set DP, it is possible to dispose the frictionplates 51 of the fourth clutch C-4 more radially outward, and toincrease the area of the friction plates. Thus, it is possible to ensuretransfer of a sufficient torque while, at the same time, reducing thenumber of friction plates 51. Furthermore, it is possible to shorten thedistance between the third and first clutches C-3, C-1 and the planetarygear unit PU and to shorten the transfer members 101, 102 of the outputside of the third and first clutches C-3, C-1, which must besufficiently strong in order to transfer a high torque. It is therebypossible to decrease the weight and to improve the controllability ofthe automatic transmission 1 ₂.

Furthermore, it is possible, for example, to supply working oil to thehydraulic servo 50 of the fourth clutch C-4 from an oil duct c50 that isprovided in the boss 3 b. Thereby, in comparison to a structure in whichthe working oil is supplied from an oil duct in the input shaft 12, itis possible to reduce the number of seal rings, to reduce the slidingresistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₂.

In addition, because the transfer member of the input side of the fourthclutch C-4 is linked to the input shaft 12 and the intermediate shaft 13at the radially inner side of the planetary gear unit PU and because aportion of the transfer member of the input side of the fourth clutchC-4 forms the clutch drum 52 of the hydraulic servo 50 of the fourthclutch C-4, there is an advantage over the case in which the transfermember of the output side of the fourth clutch C-4 forms the clutch drumof the hydraulic servo 50 in that, in the present embodiment, the clutchdrum of the hydraulic servo 50 serves to transfer power from the inputshaft 12, and thus it is possible to make the transfer member shorter(more axially compact).

Furthermore, because the counter gear 15 is located axially intermediatethe planetary gear unit PU and the planetary gear set DP, becausesupport member 120 a is provided to support the counter gear 15, becausethe hub member 112 of the second clutch C-2 is linked to the carrier CR1on the radially outer side of the third and first clutches C-3, C-1,because a portion of the transfer member 103 of the output side of thesecond clutch C-2 forms the clutch drum 32 of the hydraulic servo 30 ofthe second clutch C-2, and because the hydraulic servo 30 is locatedaround the support member 120 a, between the planetary gear set DP andcounter gear 15, it is possible to supply the working oil to thehydraulic servo 30 of the second clutch C-2 from an oil duct c30 in thesupport member 120 a. Thus, as compared to an embodiment in which, forexample, working oil is supplied from an oil duct in the input shaft 12,it is possible to reduce the number of seal rings, to reduce the slidingfriction of the seal rings, and to improve the power transfer efficiencyof the automatic transmission 1 ₂.

In addition, because a counter shaft 81 is arranged in parallel with theinput shaft 12 and is linked to the counter gear 15, in turn linked tothe ring gear R3, rotation output from the ring gear R3 is transferredto the counter shaft 81 via the counter gear 15, enabling use of theautomatic transmission 1 ₂ in an FF-type vehicle.

Furthermore, because the counter gear 15 is located axially intermediatethe planetary gear unit PU and the planetary gear set DP and issupported by support member 120 a, it is possible to locate the countergear 15 axially closer to the input side. For example, it is possible toposition the counter shaft portion 80 and the differential gear portion90 near the torque converter 7 side, thereby making the automatictransmission 1 ₂ more compact. Thus, it is possible to preventinterference between the transmission and the frame of the vehicle, andthereby provide more flexibility in mounting the automatic transmission1 ₂ in the vehicle.

In addition, because the carrier CR1 is linked to the input shaft 12 onthe planetary gear unit PU side of the planetary gear set DP and isaxially linked to the hub member 112, which is the transfer member ofthe input side of the second clutch C-2, on the side of the planetarygear set DP opposite the planetary gear unit PU, it is possible to linkthe carrier CR1, the transfer member 112 of the input side of the secondclutch C-2, and the input shaft 12 without a complicated configurationand to make the automatic transmission 1 ₂ more compact.

In addition, because the hub member 116 of the first brake B-1 and thetransfer member 104 that is linked thereto are axially linked to the sungear S2 on the side of the planetary gear unit PU opposite the planetarygear set DP, it is possible to link the hub member 116 of the firstbrake B-1, the transfer member 104, and the sun gear S2 without acomplicated configuration and to make the automatic transmission 1 ₂more compact.

In addition, because the planetary gear set DP includes the sun gear S1,which is normally held against rotation, a carrier CR1 that supports thepinion gear P1 and the pinion gear P2 so as to be selectively rotatableand that is normally linked to the output shaft 12, and a ring gear R1that meshes with the pinion gear P2 and outputs a reduced speedrotation, it is possible to output a reduced speed rotation, i.e.rotation at a speed less than that of the input shaft 12 from the ringgear R1.

In addition, because the planetary gear unit PU is a Ravigneaux-typeplanetary gear unit PU that includes the sun gear S2, the sun gear S3,the short pinion P3 that meshes with the sun gear S3, the long pinion P4that meshes with the sun gear S2 and meshes with the short pinion P3,the carrier CR2 that rotatably supports the short pinion P3 and the longpinion P4, and the ring gear R3 that meshes with the long pinion P4, itis possible to prevent high speed rotation of the rotary elements and toprovide advantageous gear ratios while enabling each of the rotaryelements of the planetary gear unit PU and the output side members ofeach of the clutches and brakes to be linked without making thesemembers complicated.

The first forward speed can be established by engaging the first clutchC-1 and locking the second brake B-2; the second forward speed can beestablished by engaging the first clutch C-1 and locking the first brakeB-1; the third forward speed can be established by engaging the firstclutch C-1 and the third clutch C-3; the fourth forward speed can beestablished by engaging the first clutch C-1 and the fourth clutch C-4;the fifth forward speed can be established by engaging the first clutchC-1 and the second clutch C-2; the sixth forward speed can beestablished by engaging the second clutch C-2 and the fourth clutch C-4;the seventh forward speed can be established by engaging the secondclutch C-2 and the third clutch C-3; the eighth forward speed can beestablished by engaging the second clutch C-2 and locking the firstbrake B-1; and reverse speeds can be established by engaging the thirdclutch C-3 or the fourth clutch C-4 and locking the second brake B-2.

In addition, in a velocity diagram in which the respective speeds of thesun gear S2, the sun gear S3, the carrier CR2, and the ring gear R3 ofthe planetary gear unit PU are shown on the ordinate, and thecorresponding gear ratios of the sun gear S2, the sun gear S3, andcarrier CR2, and the ring gear R3 are shown on the abscissa, a structurebecomes possible in which the sun gear S2 is positioned at the farthestleft end of the diagram and, in sequence to the right therefrom, are thecarrier CR2, the ring gear R3 that is linked to the counter gear 15, andthe sun gear S3.

Note that the automatic transmission 1 ₂ according to the secondembodiment can form an automatic transmission 1 ₇ for a vehicleaccording to a seventh embodiment described below substantially byrotating the speed change mechanism 2 ₂, whereby the relative axialpositions of units PU and DP are reversed.

Third Embodiment

Next, a third embodiment, in which a portion of the first embodiment hasbeen modified, will be explained with reference to FIG. 6 which is across-sectional view showing an automatic transmission 1 ₃. Note that inthe third embodiment described below, only the portions that differ fromthe automatic transmission 1 ₁ according to the first embodiment, willbe explained. The other portions are substantially identical, and thustheir description will be omitted.

The automatic transmission 1 ₃ according to the third embodiment has astructure that, in contrast to the automatic transmission 1 ₁ of thefirst embodiment, is modified such that the hydraulic servo 30 of thesecond clutch C-2 and the hydraulic servo 20 of the first clutch C-1 aredisposed axially intermediate the planetary gear set DP and theplanetary gear unit PU, and specifically, the hydraulic servo 30 of thesecond clutch C-2 is disposed axially intermediate the counter gear 15and the hydraulic servo 20 of the first clutch C-1 and adjacent to asupport wall 120, and the hydraulic servo 20 of the first clutch C-1 isdisposed axially intermediate the hydraulic servo 30 of the secondclutch C-2 and the hydraulic servo 40 of the third clutch C-3 on thesupport wall 120.

Specifically, in the automatic transmission 1 ₃, the hydraulic servo 40of the third clutch C-3, the hydraulic servo 20 of the first clutch C-1,the hydraulic servo 30 of the second clutch C-2, and the counter gear 15are located axially intermediate the planetary gear set DP and theplanetary gear unit PU, and the hydraulic servo 50 of the fourth clutchC-4 and the hydraulic servo 60 of the first brake B-1 are located on theside of the planetary gear unit PU that is axially opposite theplanetary gear set DP.

In the automatic transmission 1 ₃, because the fourth clutch C-4 islocated in the transfer path to connect the input shaft 12 and the sungear S2, the second clutch C-2 is located in the transfer path toconnect the carrier CR1 and the carrier CR2, and the output sidetransfer member 103 of the second clutch C-2 is linked to the axial sideof the carrier CR2 facing the planetary gear set DP, it is possible toeliminate need for a member enclosing the planetary gear unit PU.Thereby, the automatic transmission 1 ₃ can be made more radiallycompact. In addition, it is possible to shorten the transfer member thatrequires a high rigidity, to reduce the weight, and to improve thecontrollability of the automatic transmission 1 ₃. Furthermore, thisstructure facilitates the supply and discharge of lubricating oil, andensures the cooling performance. In addition, the assembly of theautomatic transmission 1 ₃ can be simplified. Furthermore, because thestructure includes a support wall 120 through which the working oil forthe clutches can be supplied, it is possible to reduce the number ofseal rings, to reduce the sliding resistance of the seal rings, and toimprove the power transfer efficiency of the automatic transmission 1 ₃.

In addition, because the hydraulic servo 30 of the second clutch C-2 isdisposed axially intermediate the planetary gear unit PU and theplanetary gear set DP, it is possible to supply working oil to thehydraulic servo 30 of the second clutch C-2 from an oil duct provided inthe support wall 120. Thereby, in comparison with a transmission inwhich the working oil is supplied from an oil duct in the input shaft12, it is possible to reduce the number of seal rings, to reduce thesliding resistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₃.

Furthermore, because the hydraulic servo 50 of the fourth clutch C-4 isdisposed on the side of the planetary gear unit PU that is axiallyopposite the planetary gear set DP, it is possible to locate thefriction plates 51 of the fourth clutch C-4 further radially outward,and to enlarge the surface area of the friction plates 51. Thereby it ispossible to ensure transfer of a sufficient torque and at the same timereduce the number of friction plates. Furthermore, it is possible tosupply working oil to the hydraulic servo 50 of the fourth clutch C-4from an oil duct provided in the boss 3 d that extends from one end ofthe case 4. Thereby, in comparison to supply of working oil from an oilduct in the input shaft 12, it is possible to reduce the number of sealrings, to reduce the sliding resistance of the seal rings, and toimprove the power transfer efficiency of the automatic transmission 1 ₃.

In addition, because the hydraulic servo 40 of the third clutch C-3 isdisposed axially intermediate the planetary gear unit PU and theplanetary gear set DP, in comparison with a structure in which thehydraulic servo 40 of the third clutch C-3 is disposed on the side ofthe planetary gear set DP that is axially opposite the planetary gearunit PU, it is possible to shorten the distance between the third clutchC-3 and the planetary gear unit PU and to shorten the output sidetransfer member 101 of the third clutch C-3, which member requiresstrength for transferring a high torque. Thereby, it is possible toreduce the weight and improve the controllability of automatictransmission 1 ₃.

In addition, because the hydraulic servo 20 of the first clutch C-1 islocated axially intermediate the planetary gear unit PU and theplanetary gear set DP, in comparison to a structure in which thehydraulic servo 20 of the third clutch C-1 is disposed on the side ofthe planetary gear set DP that is axially opposite the planetary gearunit PU, it is possible to shorten the distance between the first clutchC-1 and the planetary gear unit PU and to shorten the output sidetransfer member 102 of the first clutch C-1, which requires strength fortransferring a high torque. Thereby, it is possible to reduce the weightand to improve the controllability of the automatic transmission 1 ₃.

In addition, because of provision of a first brake B-1 that stops therotation of the sun gear S2 by locking to the case 4 and the becausehydraulic servo 60 of the first brake B-1 is disposed on the side of theplanetary gear unit PU that is axially opposite the planetary gear setDP, it is possible to link the locking force transfer member of thefirst brake B-1 and the sun gear S2 without a complicated configurationof these members and to make the automatic transmission 1 ₃ morecompact.

In the automatic transmission 1 ₃, the transfer member 103 of the outputside of the second clutch C-2 is linked to the carrier CR2 through theradially outer side of the transfer members 101, 102 of the output sideof the third and first clutches C-3, C-1, the transfer member 104 of theoutput side of the fourth clutch C-4 and the transfer member 101 of theoutput side of third clutch C-3 are connected to the sun gear S2, andthe transfer member 104 of the output side of the fourth clutch C-4, thetransfer member 101 of the output side of third clutch C-3, and the sungear S2, which rotates integrally, are disposed on the radially innerside of the transfer member 102 of the output side of the first clutchC-1. Therefore, the transfer member 104 of the output side of the fourthclutch C-4, which rotates faster than the transfer member 103 of theoutput side of the second clutch C-2, is located more radially inwardthan the transfer member 102 of the output side of the first clutch C-1,which is on the radially inner side of the transfer member 103 of theoutput side of the second clutch C-2. As a result, it is possible tomake the diameter of the transfer member 104 of the output side of thefourth clutch C-4 smaller than the diameter of the transfer member 103,and it is possible to reduce the weight as compared with a structure inwhich transfer member 104 is on the outer side. In addition, because theinertia is reduced as compared to the case in which transfer member 104is disposed on the outer side, it is possible to improve thecontrollability of the automatic transmission 1 ₃.

In addition, the third and first clutches C-3, C-1 are disposed on theside of the planetary gear set DP, the transfer members 101, 102 of theoutput side of the third and first clutches C-3, C-1 are linkedrespectively to the sun gear S2 and the sun gear S3, the fourth clutchC-4 is located on the side of the planetary gear unit PU that is axiallyopposite the planetary gear set DP, the transfer member 104 is linked tothe sun gear S2, the second clutch C-2 is disposed on the side of theplanetary gear set DP, and the transfer member 103 is linked to thecarrier CR2 through the outer side of the transfer members 101, 102.Thereby, because the transfer member 104, which rotates faster than thetransfer member 103, is on the radially inner side, the diameter of thetransfer member 104 can be made smaller than the diameter of thetransfer member 103, and it is possible to reduce the weight as comparedto a structure in which the transfer member 104 is disposed on the outerside. In addition, because inertia is reduced as compared to the case inwhich transfer member 104 is on the outside of transfer member 103, itis possible to improve the controllability of the automatic transmission1 ₃.

In addition, in comparison to a structure in which the hydraulic servo50 of the fourth clutch C-4 is located between the planetary gear unitPU and the planetary gear set DP, it is possible to locate the frictionplates 51 of the fourth clutch C-4 more radially outward, and it ispossible to increase the area of the friction plates. Thus, it ispossible to ensure transfer of a sufficient torque, and to reduce thenumber of friction plates 51. Furthermore, it is possible to shorten thedistance between the third and first clutches C-3, C-1 and the planetarygear unit PU and to shorten the transfer members 101, 102 of the outputsides of the third and first clutches C-3, C-1, which must be strong inorder to transfer a high torque. It is thereby possible to decrease theweight, and to improve the controllability of the automatic transmission1 ₃.

Furthermore, by supplying the working oil to the hydraulic servo 50 ofthe fourth clutch C-4 from an oil duct c50 in the boss 3 b, incomparison to a transmission in which the working oil is supplied froman oil duct in the input shaft 12, it is possible to reduce the numberof seal rings, to reduce the sliding resistance of the seal rings, andto improve the power transfer efficiency of the automatic transmission 1₃.

In addition, because the transfer member of the input side of the fourthclutch C-4 is linked to the input shaft 12 and the intermediate shaft 13on the inner side of the planetary gear unit PU and a portion of thetransfer member of the input side of the fourth clutch C-4 forms theclutch drum 52 of the hydraulic servo 50 of the fourth clutch C-4, incomparison to a structure in which the transfer member of the outputside of the fourth clutch C-4 forms the clutch drum of the hydraulicservo 50, the clutch drum of the hydraulic servo 50 can also serve totransfer power from the input shaft 12, and thus it is possible to formthe transfer member more axially compact.

Furthermore, because counter gear 15 is linked to the ring gear R3 andis disposed axially intermediate the planetary gear unit PU and theplanetary gear set DP, because there is an axially extending supportmember 120 a that is integral with the support wall 120 that extendsradially from the case 4 and the counter gear 15 is mounted on thesupport member 120 a, because the hub member 112 of the second clutchC-2 extends around the outer side of the third and first clutches C-3,C-1 to link with the carrier CR1, because a portion of the transfermember 103 of the output side of the second clutch C-2 forms the clutchdrum 32 of the hydraulic servo 30 of the second clutch C-2, and becausethe hydraulic servo 30 is disposed around the support member 120 abetween the planetary gear set DP and counter gear 15, it is possible tosupply the working oil to the hydraulic servo 30 of the second clutchC-2 from an oil duct c30 that is provided in the support member 120 a.Thus, in comparison to a structure in which, for example, the workingoil is supplied from an oil duct in the input shaft 12, it is possibleto reduce the number of seal rings, to reduce the sliding friction ofthe seal rings, and to improve the power transfer efficiency of theautomatic transmission 1 ₃.

In addition, the transfer member 102 of the output side of the firstclutch C-1 is connected to the sun gear S3, a portion of the transfermember 102 of the output side of the first clutch C-1 forms the clutchdrum 22 of the hydraulic servo 20 of the first clutch C-1, the hydraulicservo 20 is disposed around the support member 120 a axiallyintermediate the planetary gear set DP and the hydraulic servo 30 of thesecond clutch C-2, the transfer member 101 of the output side of thethird clutch C-3 is connected to the sun gear S2, a portion of thetransfer member 101 of the output side of the third clutch C-3 forms theclutch drum 42 of the hydraulic servo 40 of the third clutch C-3, andthe hydraulic servo 40 is disposed axially intermediate the planetarygear set DP and hydraulic servo 20 the first clutch C-1. Therefore, itis possible to supply the working oil to the hydraulic servo 20 of thefirst clutch C-1 from an oil duct c20 that runs through the support wall120 and the support member 120 a. Thus, in comparison to a structure inwhich, for example, the working oil is supplied from an oil duct in theinput shaft 12, it is possible to reduce the number of seal rings, toreduce the sliding resistance of the seal rings, and to improve thepower transfer efficiency of the automatic transmission 1 ₃. Inaddition, because the hydraulic servo 40 of the third clutch C-3 islocated axially intermediate the planetary gear unit PU and theplanetary gear set DP, in comparison to a structure in which, forexample, the hydraulic servo 40 of the third clutch C-3 is disposed onthe side of the planetary gear set DP that is axially opposite theplanetary gear unit PU, it is possible to shorten the distance betweenthe third clutch C-3 and the planetary gear unit PU and to shorten thetransfer member 101 of the output side of the third clutch C-3 whichmust be strong in order to transfer high torque. It is thereby possibleto reduce the weight and to improve the controllability of the automatictransmission.

Furthermore, because counter shaft 81 is arranged in parallel with theinput shaft 12 and linked via the counter gear 15 that is linked to thering gear R3 and because the output rotation from the ring gear R3 istransferred to the counter shaft 81 via the counter gear 15, it ispossible to advantageously use the automatic transmission 1 ₃ in anFF-type vehicle.

In addition, because the counter gear 15 is disposed axiallyintermediate the planetary gear unit PU and the planetary gear set DPand is supported by a support member 120 a that is integral with thesupport wall 120 that extends from the case 4, it is possible to locatethe counter gear 15 axially closer to the input side. For example, it ispossible to locate the counter shaft portion 80 and the differentialgear portion 90 near the torque converter 7, thereby making theautomatic transmission 1 ₃ more compact. Thus, it is possible to preventinterference between the transmission and the frame of the vehicle, andit is possible to facilitate the mounting of the automatic transmission1 ₃ in the vehicle.

Furthermore, because the carrier CR1 is linked to the input shaft 12 onthe side of to the planetary gear set DP facing the planetary gear unitPU and is linked to the hub member 112, which is the transfer member ofthe input side of the second clutch C-2, on the side of the planetarygear set DP that is axially opposite the planetary gear unit PU, it ispossible to link the carrier CR1, the transfer member 112 of the inputside of the second clutch C-2, and the input shaft 12 without need forany complicated configuration of these components, and to make theautomatic transmission 1 ₃ more compact.

In addition, because the hub member 116 of the first brake B-1 and thetransfer member 104 are axially connected to the sun gear S2 on the sideof the planetary gear unit PU that is axially opposite the planetarygear set DP, it is possible to link the hub member 116 of the firstbrake B-1, the transfer member 104, and the sun gear S2 withoutcomplicated configuration, and to make the automatic transmission 1 ₃more compact.

In addition, because the planetary gear set DP includes a sun gear S1which is normally held against rotation, a carrier CR1 that rotatablysupports the pinion gear P1 and the pinion gear P2 and is coupled to theinput shaft 12, and a ring gear R1 that meshes with the pinion gear P2and outputs a reduced speed rotation, it is possible to output from thering gear R1 a reduced speed rotation slower than the input rotation ofthe input shaft 12.

In addition, because the planetary gear unit PU is a Ravigneaux-typeplanetary gear unit PU that includes a sun gear S2, a sun gear S3, shortpinion P3 that meshes with the sun gear S3, a long pinion P4 that mesheswith the sun gear S2 and with the short pinion P3, a carrier CR2 thatrotatably supports the short pinion P3 and the long pinion P4, and thering gear R3 that meshes with the long pinion P4, it is possible toprevent high speed rotation of each of the rotary members and to providefavorable gear ratios while enabling each of the rotary elements of theplanetary gear unit PU and the output side members of each of theclutches and brakes to be linked without any complicated structure.

The first forward speed can be established by engaging the first clutchC-1 and locking the second brake B-2; the second forward speed can beestablished by engaging the first clutch C-1 and locking the first brakeB-1; the third forward speed can be established by engaging the firstclutch C-1 and the third clutch C-3; the fourth forward speed can beestablished by engaging the first clutch C-1 and the fourth clutch C4;the fifth forward speed can be established by engaging the first clutchC-1 and the second clutch C-2; the sixth forward speed is established byengaging the second clutch C-2 and the fourth clutch C-4; the seventhforward speed is established by engaging the second clutch C-2 and thethird clutch C-3; the eighth forward speed is established by engagingthe second clutch C-2 and locking the first brake B-1; and reversespeeds are established by engaging the third clutch C-3 or the fourthclutch C-4 and locking the second brake B-2.

In addition, in a velocity diagram in which the respective speeds of thesun gear S2, the sun gear S3, the carrier CR2, and the ring gear R3 ofthe planetary gear unit PU are shown on the ordinate, and thecorresponding gear ratios of the sun gear S2, the sun gear S3, thecarrier CR2, and the ring gear R3 are shown on the abscissa, the sungear S2 is positioned at the left end of the abscissa and the carrierCR2, the ring gear R3 that is linked to the counter gear 15, and the sungear S3 are arranged in sequence to the right.

Note that the automatic transmission 1 ₃ according to the thirdembodiment can form the automatic transmission 1 ₈ according to aneighth embodiment described below by rotating the speed change mechanism2 ₃ left-right.

Fourth Embodiment

Next, a fourth embodiment, in which a portion of the first embodimenthas been modified, will be explained with reference to FIG. 7 which is across-section of an automatic transmission 1 ₄ according to the fourthembodiment. Note that in describing the fourth embodiment below, onlythose features that differ from the automatic transmission 1 ₁ accordingto the first embodiment will be explained. The other features aresubstantially identical and thus their explanations will be omitted.

The automatic transmission 1 ₄ of the fourth embodiment is amodification to the automatic transmission 1 ₁ of the first embodiment,wherein the hydraulic servo 30 of the second clutch C-2 and thehydraulic servo 20 of the first clutch C-1 are located axiallyintermediate the planetary gear set DP and the planetary gear unit PU,and the hydraulic servo 40 of the third clutch C-3 is disposed on theside of the planetary gear set DP that is axially opposite the planetarygear unit PU. Specifically, the hydraulic servo 30 of the second clutchC-2 is located axially intermediate the counter gear 15 and thehydraulic servo 20 of the first clutch C-1 and adjacent to a supportwall 120, the hydraulic servo 20 of the first clutch C-1 is located onthe support wall 120, axially intermediate the hydraulic servo 30 of thesecond clutch C-2 and the planetary gear set DP, and the hydraulic servo40 of the third clutch C-3 is located on the boss 3 b.

Specifically, in this automatic transmission 1 ₄, the hydraulic servo 40of the third clutch C-3 is located on the side of the planetary gear setDP that is axially opposite the planetary gear unit PU. The hydraulicservo 20 of the first clutch C-1, the hydraulic servo 30 of the secondclutch C-2, and the counter gear 15 are located axially intermediate theplanetary gear set DP and the planetary gear unit PU, and the hydraulicservo 50 of the fourth clutch C-4 and the hydraulic servo 60 of thefirst brake B-1 are located on the side of the planetary gear unit PUthat is axially opposite the planetary gear set DP.

In the automatic transmission 1 ₄ described above, because the fourthclutch C4 is interposed in the transfer path to selectively connect theinput shaft 12 and the sun gear S2, because the second clutch C-2 isinterposed in the transfer path to selectively connect the carrier CR1and the carrier CR2, and because the output side transfer member 103 ofthe second clutch C-2 is linked to the carrier CR2 at the side facingthe planetary gear set DP, need for a member enclosing the planetarygear unit PU is eliminated and the automatic transmission 1 ₄ can bemore radially compact. In addition, it is possible to shorten thetransfer member that requires a high rigidity, to reduce the weight, andto improve the controllability of the automatic transmission 1 ₄.Furthermore, the structure allows the lubricating oil to be readilydischarged, and the cooling performance to be ensured. In addition, theassembly of the automatic transmission 1 ₄ is simplified. Furthermore,because the working oil for the clutches can be supplied from supportwall 120 due to the configuration of each of the clutches, it ispossible to reduce the number of seal rings, to reduce the slidingresistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₄.

In addition, because the hydraulic servo 30 of the second clutch C-2 islocated axially intermediate the planetary gear unit PU and theplanetary gear set DP, it is possible to supply the working oil to thehydraulic servo 30 of the second clutch C-2 from an oil duct that isprovided in the support wall 120. Thereby, in comparison to a structurein which the working oil is supplied from an oil duct in the input shaft12, it is possible to reduce the number of seal rings, to reduce thesliding resistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₄.

Furthermore, because the hydraulic servo 50 of the fourth clutch C4 isdisposed on the side of the planetary gear unit PU that is axiallyopposite the planetary gear set DP, it is possible to locate thefriction plates 51 of the fourth clutch C-4 on the radially outer sideand to enlarge the surface area of the friction plates 51, and thus, itis possible to ensure transfer of a sufficient torque, while reducingthe number of friction plates. Furthermore, because working oil issupplied to the hydraulic servo 50 of the fourth clutch C-4 from an oilduct in the boss 3 d. In comparison to a structure in which the workingoil is supplied from an oil duct in the input shaft 12, it is possibleto reduce the number of seal rings, to reduce the sliding resistance ofthe seal rings, and to improve the power transfer efficiency of theautomatic transmission 1 ₄.

In addition, because the hydraulic servo 40 of the third clutch C-3 isdisposed on the side of the planetary gear set DP that is axiallyopposite the planetary gear unit PU, it is possible to supply theworking oil to the hydraulic servo 40 of the third clutch C-3 from anoil duct in the boss 3 b. Thereby, as compared to a structure whereinthe working oil is supplied from an oil duct in the input shaft 12, itis possible to reduce the number of seal rings, to reduce the slidingresistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₄.

Furthermore, because the hydraulic servo 20 of the first clutch C-1 islocated axially intermediate the planetary gear set DP and the planetarygear unit PU, in comparison to a structure in which the hydraulic servo20 of the first clutch C-1 is disposed on the side of the planetary gearset DP that is axially opposite the planetary gear unit PU, it ispossible to shorten the distance between the first clutch C-1 and theplanetary gear unit PU, to shorten the output side transfer member 102of the first clutch C-1, which must be strong in order to transfer hightorque, to reduce weight, and to improve the controllability of theautomatic transmission 1 ₄.

In addition, because a first brake B-1 selectively locks the sun gear S2against rotation and the hydraulic servo 60 of the first brake B-1 isdisposed on the side of planetary gear unit PU that is axially oppositethe planetary gear set DP, the locking force transfer member of thefirst brake B-1 and the sun gear S2 can be linked without a complicatedconfiguration, and it is possible to make the automatic transmission 1 ₄more compact.

In the automatic transmission 1 ₄ according to the present invention,the transfer member 103 of the output side of the second clutch C-2 ison the radially outer side of the transfer members 101, 102 of theoutput side of the third and first clutches C-3, C-1, the transfermember 104 of the output side of the fourth clutch C-4 and the transfermember 101 of the output side of third clutch C-3 are linked to the sungear S2, and the transfer member 104 of the output side of the fourthclutch C-4, the transfer member 101 of the output side of third clutchC-3, and the sun gear S2, which rotate integrally, are radially inwardof the transfer member 102 of the output side of the first clutch C-1.Therefore, the transfer member 104, which rotates faster than thetransfer member 103, is located more radially inward than the transfermember 102, which is on the radially inner side of the transfer member103. As a result, it is possible to make the diameter of the transfermember 104 smaller than the diameter of the transfer member 103, and itis possible to reduce weight as compared to a structure in whichtransfer member 104 is on the radially outer side. In addition, becausethe inertia is reduced in comparison to a structure in which transfermember 104 is located on the radially outer side, it is possible toimprove the controllability of the automatic transmission 1 ₄.

The third and first clutches C-3, C-1 are located on the planetary gearset DP side relative to the planetary gear set PU, the transfer members101, 102 of the output side of the third and first clutches C-3, C-1 arelinked respectively to the sun gear S2 and the sun gear S3, the fourthclutch C4 is located on the side of the planetary gear unit PU that isaxially opposite the planetary gear set DP, the transfer member 104 ofthe output side of the fourth clutch C-4 is linked to the sun gear S2,the second clutch C-2 is disposed on the planetary gear set DP siderelative to the planetary unit PU, and the transfer member 103 is linkedto the carrier CR2 on the radially outer side of the transfer members101, 102. Because the transfer member 104 of the output side of thefourth clutch C-4, which rotates faster than the transfer member of theoutput side of the second clutch C-2, is on the radially inner side, thediameter of the transfer member 104 is smaller than the diameter of thetransfer member 103, and it is possible to reduce the weight as comparedto a structure in which transfer member 104 is disposed on the radiallyouter side. In addition, because it is possible to reduce the inertia ascompared to a structure in which transfer member 104 is on the outside,it is possible to improve the controllability of the automatictransmission 1 ₄.

In addition, in comparison to a structure in which the hydraulic servo50 of the fourth clutch C-4 is located between the planetary gear unitPU and the planetary gear set DP, it is possible to locate the frictionplates 51 of the fourth clutch C-4 more radially outward, and toincrease the area of the friction plates. Thus, it is possible to ensuretransfer of a sufficient torque, and to reduce the number of frictionplates 51. Furthermore, it is possible to shorten the distance betweenthe third and first clutches C-3, C-1 and the planetary gear unit PU,and to shorten the transfer members 101, 102 of the output side of thethird and first clutches C-3, C-1, which must be strong in order totransfer a high torque. It is thereby possible to decrease the weightand to improve the controllability of the automatic transmission 1 ₄.

The working oil to the hydraulic servo 50 of the fourth clutch C-4 issupplied from an oil duct c50 in the boss 3 b. Thereby, in comparison toa structure in which the working oil is supplied from an oil duct in theinput shaft 12, it is possible to reduce the number of seal rings, toreduce the sliding resistance of the seal rings, and to improve thepower transfer efficiency of the automatic transmission 1 ₄.

In addition, because the transfer member of the input side of the fourthclutch C-4 is linked to the input shaft 12 and the intermediate shaft 13on the inner side of the planetary gear unit PU and a portion of thetransfer member of the input side of the fourth clutch C-4 forms theclutch drum 52 of the hydraulic servo 50 of the fourth clutch C-4, ascompared to the case in which the transfer member of the output side ofthe fourth clutch C-4 forms the clutch drum of the hydraulic servo 50,the clutch drum of the hydraulic servo 50 can also serve as a transfermember that transfers power from the input shaft 12, and thus it ispossible to make the transfer member more axially compact.

Furthermore, because counter gear 15 is linked to the ring gear R3, islocated axially intermediate the planetary gear unit set PU and theplanetary gear set DP and is mounted on a support member 120 a, becausethe hub member 112 of the second clutch C-2 is linked to the carrier CR1on the radially outer side of the third and first clutches C-3, C-1,because a portion of the transfer member 103 of the output side of thesecond clutch C-2 forms the clutch drum 32 of the hydraulic servo 30 ofthe second clutch C-2, and because the hydraulic servo 30 is disposedaround the support member 120 a between the planetary gear set DP andcounter gear 15, it is possible to supply the working oil to thehydraulic servo 30 of the second clutch C-2 from an oil duct c30 in thesupport member 120 a. Thus, in comparison to a structure in which, forexample, the working oil is supplied from an oil duct in the input shaft12, it is possible to reduce the number of seal rings, to reduce thesliding friction of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₄.

The boss 3 b extends from the side wall 3 a of the case 4 and holds thesun gear S1 stationary. The transfer member of the input side of thethird clutch C-3 is linked to the ring gear R1, a portion thereof formsthe clutch drum 42 of the hydraulic servo 40 of the third clutch C-3.The hydraulic servo 40 is located on the boss 3 b axially intermediatethe planetary gear set DP and the side wall 3 a. The transfer member ofthe input side of the first clutch C-1 is linked to the transfer memberof the input side of the third clutch C-3, and a portion thereof formsthe clutch drum 22 of the hydraulic servo 20 of the first clutch C-1,the hydraulic servo 20 being mounted on the support member 120 a axiallyintermediate the planetary gear set DP and the hydraulic servo 30 of thesecond clutch C-2. Therefore, it is possible to supply the working oilto the hydraulic servo 40 of the third clutch C-3 from an oil duct c40in the boss 3 b. Thus, in comparison to a structure in which thehydraulic servo 40 of the third clutch C-3 is arranged around the inputshaft 12 spaced from the boss 3 b and the working oil is supplied via anoil duct in the input shaft 12, it is possible to shorten the length ofthe oil duct by an amount equivalent to the length of the oil duct inthe input shaft 12 which is eliminated, and it is possible to improvethe controllability of the automatic transmission 1 ₄. Because theworking oil is supplied to the hydraulic servo 20 of the first clutchC-1 from an oil duct c20 extending through the support wall 120 and thesupport member 120 a, as compared to a structure in which, for example,the working oil is supplied from an oil duct in the input shaft 12, itis possible to reduce the number of seal rings, to reduce the slidingresistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₄.

Because counter shaft 81 is arranged in parallel with the input shaft 12and is linked via the counter gear 15 to the ring gear R3 and the outputrotation from the ring gear R3 is transferred to the counter shaft 81via the counter gear 15, it is possible to advantageously use theautomatic transmission 1 ₄ in an FF-type vehicle.

In addition, because the counter gear 15 is located axially intermediatethe planetary gear unit PU and the planetary gear set DP and issupported by support member 120 a, it is possible to locate the countergear 15 closer to the input side. For example, it is possible toposition the counter shaft portion 80 and the differential gear portion90 near the torque converter 7 side, and to thereby make the automatictransmission 1 ₄ more compact and to prevent interference between thetransmission, differential, etc. and the frame of the vehicle, and tofacilitate the mounting of the automatic transmission 1 ₄ in thevehicle.

Furthermore, because the carrier CR1 is linked to the input shaft 12 onthe planetary gear unit PU relative to the planetary gear set DP and isaxially linked to the hub member 112, which is the transfer member ofthe input side of the second clutch C-2, on the side of the planetarygear set DP that is axially opposite the planetary gear unit PU, it ispossible to link the carrier CR1, the transfer member 112 of the inputside of the second clutch C-2, and the input shaft 12 without making anycomplicated configuration, and it is possible to make the automatictransmission 1 ₄ more compact.

In addition, because the hub member 116 of the first brake B-1 and thetransfer member 104 are axially linked to the sun gear S2 on the side ofthe planetary gear unit PU that is axially opposite the planetary gearset DP, it is possible to link the hub member 116 of the first brakeB-1, the transfer member 104, and the sun gear S2 without making thesemembers complicated, and to make the automatic transmission 1 ₄ morecompact.

The planetary gear set DP includes the sun gear S1, which is normallyheld stationary, a carrier CR1 that rotatably supports the pinion gearP1 and the pinion gear P2 and that is coupled to the output shaft 12,and a ring gear R1 that meshes with the pinion gear P2 and outputs areduced speed rotation. Therefore, it is possible to output rotation ata reduced speed, relative to the input rotation of the input shaft 12,from the ring gear R1.

In addition, because the planetary gear unit PU is a Ravigneaux-typeplanetary gear unit PU that includes the sun gear S2, the sun gear S3,the short pinion P3 that meshes with the sun gear S3, the long pinion P4that meshes with the sun gear S2 and meshes with the short pinion P3,the carrier CR2 that rotatably supports the short pinion P3 and the longpinion P4, and the ring gear R3 that meshes with the long pinion P4, itis possible to prevent high speed rotation of each of the rotaryelements and to provide advantageous gear ratios while enabling each ofthe rotary elements of the planetary gear unit PU and the output sidemembers of each of the clutches and brakes to be linked without anycomplicated configuration.

The first forward speed can be established by engaging the first clutchC-1 and locking the second brake B-2; the second forward speed can beestablished by engaging the first clutch C-1 and locking the first brakeB-1; the third forward speed can be established by engaging the firstclutch C-1 and the third clutch C-3; the fourth forward speed can beestablished by engaging the first clutch C-1 and the fourth clutch C-4;the fifth forward speed can be established by engaging the first clutchC-1 and the second clutch C-2; the sixth forward speed can beestablished by engaging the second clutch C-2 and the fourth clutch C-4;the seventh forward speed can be established by engaging the secondclutch C-2 and the third clutch C-3; the eighth forward speed can beestablished by engaging the second clutch C-2 and locking the firstbrake B-1; and reverse speeds can be established by engaging the thirdclutch C-3 or the fourth clutch C-4 and locking the second brake B-2.

In a velocity diagram in which the respective speeds of the sun gear S2,the sun gear S3, the carrier CR2, and the ring gear R3 of the planetarygear unit PU are shown on the ordinate, and the corresponding gearratios of the sun gear S2, the sun gear S3, and carrier CR2, and thering gear R3 are shown on the abscissa, the sun gear S2 is positioned atthe far left end of the abscissa and, in sequence from the left, are thecarrier CR2, the ring gear R3 that is linked to the counter gear 15, andthe sun gear S3.

Note that if the speed change mechanism 2 ₄ of the automatictransmission 1 ₄ of the fourth embodiment is rotated left-right 180°,the result is the automatic transmission 1 ₉ of the ninth embodiment.

Fifth Embodiment

Next, a fifth embodiment, in which a portion of the first embodiment ismodified, will be explained with reference to FIG. 8 to FIG. 10. Indescribing the fifth embodiment, only those features that differ fromthe automatic transmission 1 ₁ according to the first embodiment will beexplained. The other features/components are substantially identical,and their description will be omitted.

The automatic transmission 1 ₅ of the fifth embodiment differs from theautomatic transmission 1 ₁ of the first embodiment, in that thehydraulic servo 30 of the second clutch C-2, the hydraulic servo 20 ofthe first clutch C-1, and the hydraulic servo 50 of the fourth clutchC-4 are all located axially intermediate the planetary gear set DP andthe planetary gear unit PU, and the hydraulic servo 40 of the thirdclutch C-3 is located on the side of the planetary gear set DP that isaxially opposite the planetary gear unit PU. Specifically, the hydraulicservo 30 of the second clutch C-2 is located axially intermediate thecounter gear 15 and the hydraulic servo 20 of the first clutch C-1 andadjacent the support wall 120, the hydraulic servo 20 of the firstclutch C-1 is located on the support member 120 a axially intermediatethe hydraulic servo 30 of the second clutch C-2 and the hydraulic servo50 of the fourth clutch C-4, the hydraulic servo 50 of the fourth clutchC-4 is located axially intermediate the hydraulic servo 20 of the firstclutch C-1 and the planetary gear set DP, and the hydraulic servo 40 ofthe third clutch C-3 is located on the boss 3 b.

Specifically, in the automatic transmission 1 ₅, the hydraulic servo 40of the third clutch C-3 is disposed on the side of the planetary gearset DP that is axially opposite the planetary gear unit PU. Thehydraulic servo 50 of the fourth clutch C-4, the hydraulic servo 20 ofthe first clutch C-1, the hydraulic servo 30 of the second clutch C-2,and the counter gear 15 are located axially intermediate the planetarygear set DP and the planetary gear unit PU, and the hydraulic servo 60of the first brake B-1 is disposed on the side of the planetary gearunit PU that is axially opposite the planetary gear set DP.

Because the fourth clutch C-4 is on the input shaft 12, it is possibleto eliminate continuous transfer of the input rotation to theintermediate shaft 13. Thus, the input shaft 12 and the intermediateshaft 13 can be separated so as to selectively rotate relative to eachother, the intermediate shaft 13 can be used as a power transfer memberthat transfers the reduced speed rotation from the third clutch C-3 andthe input rotation from the fourth clutch C-4, that is, the intermediateshaft 13 can receive rotation from both the output side transfer member101 of the third clutch C-3 and the output side transfer member 104 ofthe fourth clutch C-4. Thereby, in comparison to a structure in whichthe transfer member 101 is covered on the intermediate shaft 13, it ispossible to reduce the sliding resistance, and it is possible to improvethe transfer efficiency of the automatic transmission 1 ₅.

As shown in FIG. 8 and FIG. 9, the second brake B-2 is what is termed aband brake that locks the clutch drum 32 of the second clutch C-2 to thecase 4 by tightening a brake band 171 on the clutch drum 32, and isprovided with a one-way clutch F-1 that restricts the rotation of thecarrier CR2 of the planetary gear unit PU to one direction.

In the D (drive) range and in the first forward speed (1st), as shown inFIG. 10, the first clutch C-1 and the one-way clutch F-1 are engaged.Thus, as shown in FIG. 9 (and also refer to FIG. 5), the rotation of thering gear R1, at a speed which is reduced by the sun gear S1, which isstationary, and the carrier CR1, which provides the input rotation, isinput to the sun gear S3 via the first clutch C-1. In addition, therotation of the carrier CR2 is restricted to one direction (the normalrotation direction), that is, the reverse rotation of the carrier CR2 isprevented and held stationary. Thereby, the reduced speed rotation thatis input to the sun gear S3 is output to the ring gear R3 via thecarrier CR2, which is stationary, and the normal rotation is output fromthe counter gear 15 as the first forward speed.

During engine braking (i.e., during coasting), by locking the secondbrake B-2, holding the carrier CR2 stationary, and preventing the normalrotation of this carrier CR2, the state of the first forward speed ismaintained. In addition, in the first forward speed, because the reverserotation of the carrier CR2 is prevented by the one-way clutch F-1 andnormal rotation is permitted, establishing the first forward speed when,for example, switching from a non-travel range to a travel range, issmoothly effected by the automatic engagement of the one-way clutch F-1.

Because the second through eighth forward speeds, the first reversespeed, and the second reverse speed are established in a manneridentical to the first embodiment, the explanations thereof are omitted.

In the automatic transmission 1 ₅ described above, because the fourthclutch C4 is arranged in the transfer path to connect the input shaft 12and the sun gear S2 (See FIG. 9), the second clutch C-2 is arranged inthe transfer path to connect the carrier CR1 and the carrier CR2, andthe output side transfer member 103 of the second clutch C-2 is linkedto the side of the carrier CR2 axially facing the planetary gear set DP,it is possible to avoid use of a member enclosing the planetary gearunit PU, whereby the automatic transmission 1 ₅ can be made moreradially compact. In addition, it is possible to shorten the transfermember that requires a high rigidity, to reduce the weight, and toimprove the controllability of the automatic transmission 1 ₅.Furthermore, the structure allows the supplied lubricating oil to bereadily discharged onto lubricating points, and the cooling performanceis ensured. In addition, the assembly of the automatic transmission 1 ₅can be simplified. Furthermore, because the working oil for the clutchescan be supplied from support wall 120 due to the configuration of eachof the clutches, it is possible to reduce the number of seal rings, toreduce the sliding resistance of the seal rings, and to improve thepower transfer efficiency of the automatic transmission 1 ₅.

In addition, because the hydraulic servo 30 of the second clutch C-2 islocated axially intermediate the planetary gear unit PU and theplanetary gear set DP, it is possible to supply working oil to thehydraulic servo 30 of the second clutch C-2 from an oil duct provided inthe support wall 120. Whereby, in comparison to a structure in which theworking oil is supplied from an oil duct in the input shaft 12, it ispossible to reduce the number of seal rings, to reduce the slidingresistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₅.

In addition, because the hydraulic servo 50 of the fourth clutch C-4 islocated axially intermediate the planetary gear unit PU and theplanetary gear set DP and adjacent to the planetary gear set DP, aportion of the carrier CR1 and the clutch drum 52 of the hydraulic servo50 of the fourth clutch C-4 can be formed as a single member, (that is,the clutch drum 52 and the side plate of the carrier CR1) and thus it ispossible to reduce both size and weight.

Furthermore, because the hydraulic servo 40 of the third clutch C-3 islocated on the side of the planetary gear set DP that is axiallyopposite the planetary gear unit PU, it is possible to supply workingoil to the hydraulic servo 40 of the third clutch C-3 from an oil ductprovided in the boss 3 b that axially extends from one end of the case4. Thereby, in comparison to a structure in which working oil issupplied from an oil duct provided in the input shaft 12, it is possibleto reduce the number of seal rings, to reduce the sliding resistance ofthe seal rings, and to improve the power transfer efficiency of theautomatic transmission 1 ₅.

In addition, because the hydraulic servo 20 of the first clutch C-1 islocated on the side of the planetary gear unit PU that is axiallyopposite the planetary gear set DP, it is possible to supply working oilto the hydraulic servo 20 of the first clutch C-1 from an oil ductprovided in the support wall 120. Whereby, in comparison to a structurein which working oil is supplied from an oil duct in the input shaft 12,it is possible to reduce the number of seal rings, and to reduce thesliding resistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₅.

Furthermore, because a first brake B-1 that selectively locks the sungear S2 to the case 4 and the hydraulic servo 60 of the first brake B-1is located on the side of planetary gear unit PU that is axiallyopposite the planetary gear set DP, the locking force transfer member ofthe first brake B-1 and the sun gear S2 can be linked without acomplicated structure, and it is possible to make the automatictransmission 1 ₅ more compact.

In the automatic transmission 1 ₅, the transfer member 103 of the outputside of the second clutch C-2, which is linked to the carrier CR2, is onthe radially outer side of the transfer members 101, 102, theintermediate shaft 13, which in this embodiment is the transfer memberof the output side of the fourth clutch C-4, and the transfer member 101of the output side of third clutch C-3 are linked to the sun gear S2.The intermediate shaft 13, the transfer member 101 of the output side ofthird clutch C-3, and the sun gear S2, which rotate integrally, areradially inward of the transfer member 102 of the output side of thefirst clutch C-1. Therefore, the intermediate shaft 13, which is thetransfer member of the output side of the fourth clutch C-4, whichrotates faster than the transfer member 103 of the output side of thesecond clutch C-2, is more radially inward than the transfer member 102of the output side of the first clutch C-1, which is on the innercircumferential side of the transfer member 103 of the output side ofthe second clutch C-2. Thus, it is possible to make the diameter of theintermediate shaft 13 smaller than the diameter of the transfer member103, and to reduce weight as compared with a structure in which transfermember 104 is on the radially outer side. In addition, because theinertia is reduced in comparison to a structure in which the transfermember 104 is located on the radially outer side, it is possible toimprove the controllability of the automatic transmission 1 ₅.

In addition, the third and first clutches C-3, C-1 are disposed on theplanetary gear unit PU side of the planetary gear set DP, the transfermembers 101, 102 of the output side of the third and first clutches C-3,C-1 are linked respectively to the sun gear S2 and the sun gear S3, thefourth clutch C-4 is located on the side of the planetary gear unit PUthat is axially opposite the planetary gear set DP, the intermediateshaft 13 is linked to the sun gear S2, the second clutch C-2 is locatedaxially intermediate planetary gear set DP and the planetary unit PU,and the transfer member 103 of the output side of the second clutch C-2which is linked to the carrier CR2 axially extends radially outward ofthe transfer members 101, 102. Thereby, the intermediate shaft 13 whichrotates faster than the transfer member of the output side of the secondclutch C-2, is on the radially inner side. Thus, the diameter of theintermediate shaft 13 can be made smaller than the diameter of thetransfer member 103, thus reducing the weight as compared to a structurein which the transfer member 13 (here, the intermediate shaft) isdisposed on the radially outer side. In addition, because it is possibleto reduce the inertia in comparison to a structure in which transfermember 104 is on the outside, it is possible to improve thecontrollability of the automatic transmission 1 ₅.

Furthermore, because the transfer member of the input side of the fourthclutch C-4 is directly linked to the carrier CR1 and a portion of thecarrier CR1 serves as a portion of the hydraulic servo 50 of the fourthclutch C-4, it is possible to use the portions of the carrier CR1 andthe hydraulic servo 50 of the fourth clutch C-4 (that is, a portion ofthe clutch drum 52 and the side plate of the carrier CR1) in common, andto thereby reduce the weight and size.

Counter gear 15 is linked to the ring gear R3 and is located axiallyintermediate the planetary gear unit PU and the planetary gear set DP. Asupport member 120 a is integral with the support wall 120 that extendsfrom the case 4 and supports the counter gear 15. The hub member 112 ofthe second clutch C-2 is linked to the carrier CR1 through the radiallyouter side of the third and first clutches C-3, C-1. A portion of thetransfer member 103 of the output side of the second clutch C-2 formsthe clutch drum 32 of the hydraulic servo 30 of the second clutch C-2,and the hydraulic servo 30 is located on the support member 120 abetween the planetary gear set DP and counter gear 15. Therefore, it ispossible to supply the working oil to the hydraulic servo 30 of thesecond clutch C-2 from an oil duct c30 in the support member 120 a.Thus, in comparison to a structure in which, for example, the workingoil is supplied from an oil duct in the input shaft 12, it is possibleto reduce the number of seal rings, to reduce the sliding friction ofthe seal rings, and to improve the power transfer efficiency of theautomatic transmission 1 ₅.

Furthermore, there is a boss 3 b that holds the sun gear S1 stationary,the transfer member of the input side of the third clutch C-3 is linkedto the ring gear R1 and a portion of the transfer member of the inputside of the third clutch C-3 forms the clutch drum 42 of the hydraulicservo 40 of the third clutch C-3, the hydraulic servo 40 is located onthe boss 3 b axially intermediate the planetary gear set DP and the sidewall 3 a, the transfer member of the input side of the first clutch C-1is linked to the transfer member of the input side of the third clutchC-3 and a portion of the transfer member of the input side of the firstclutch C-1 forms the clutch drum 22 of the hydraulic servo 20 of thefirst clutch C-1, and the hydraulic servo 20 is located on the supportmember 120 a axially intermediate the planetary gear set DP and thehydraulic servo 30 of the second clutch C-2. Therefore, it is possibleto supply the working oil to the hydraulic servo 40 of the third clutchC-3 from an oil duct c40 in the boss 3 b. Thus, in comparison to astructure in which, for example, the hydraulic servo 40 of the thirdclutch C-3 is arranged on the input shaft 12 spaced from the boss 3 band the working oil is supplied via an oil duct in the input shaft 12,it is possible to shorten the length of the oil duct by an amountequivalent to the length of an oil duct in the input shaft 12, and thecontrollability of the automatic transmission 1 ₅ is thereby improved.In addition, working oil is supplied to the hydraulic servo 20 of thefirst clutch C-1 from an oil duct c20 extending through the support wall120 and the support member 120 a. Thus, in comparison to a structure inwhich the working oil is supplied from an oil duct in the input shaft12, it is possible to reduce the number of seal rings, to reduce thesliding resistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₅.

In addition, because counter shaft 81 is arranged in parallel with theinput shaft 12 and is linked via the counter gear 15, in turn linked tothe ring gear R3, and the output rotation from the ring gear R3 istransferred to the counter shaft 81 via the counter gear 15, it ispossible to use the automatic transmission 1 ₅ advantageously in anFF-type vehicle.

Furthermore, because the counter gear 15 is located axially intermediatethe planetary gear unit PU and the planetary gear set DP and issupported on support member 120 a, it is possible to position thecounter gear 15 axially closer to the input side. For example, it ispossible to position the counter shaft portion 80 and the differentialgear portion 90 near the torque converter 7 side, and it is possible tomake the automatic transmission 1 ₅ more compact. Thereby, it ispossible to prevent interference between the transmission differential,etc. and the frame of the vehicle, and to facilitate the mounting of theautomatic transmission 1 ₅ in the vehicle.

In addition, because the carrier CR1 is linked to the input shaft 12 onthe planetary gear unit PU side of the planetary gear set DP and isaxially linked to the hub member 112, which serves as the transfermember of the input side of the second clutch C-2, on the side of theplanetary gear set DP that is axially opposite the planetary gear unitPU, it is possible to link the carrier CR1, the transfer member 112 ofthe input side of the second clutch C-2, and the input shaft 12 withoutmaking these members complicated, and to make the automatic transmission1 ₅ more compact.

In addition, because the hub member 116 of the first brake B-1 and thetransfer member 104, that is linked thereto, are axially linked to thesun gear S2 on the side of the planetary gear unit PU that is axiallyopposite the planetary gear set DP, it is possible to link the hubmember 116 of the first brake B-1, the transfer member 104, and the sungear S2 without a component of a complicated configuration, and it ispossible to make the automatic transmission 1 ₅ more compact.

In addition, because the planetary gear set DP includes the sun gear S1,which is normally held so as not to rotate, a carrier CR1 that rotatablysupports the pinion gear P1 and the pinion gear P2 and that is coupledto the input shaft 12, and a ring gear R1 that meshes with the piniongear P2 and outputs a reduced speed rotation, it is possible to output areduced speed rotation, as compared to speed of the input rotation ofthe input shaft 12, from the ring gear R1.

In addition, because the planetary gear unit PU is a Ravigneaux-typeplanetary gear unit PU that includes the sun gear S2, the sun gear S3,the short pinion P3 that meshes with the sun gear S3, the long pinion P4that meshes with the sun gear S2 and with the short pinion P3, thecarrier CR2 that rotatably supports the short pinion P3 and the longpinion P4, and the ring gear R3 that meshes with the long pinion P4, itis possible to prevent high speed rotation of each of the rotaryelements and to provide advantageous gear ratios while enabling each ofthe rotary elements of the planetary gear unit PU and the output sidemembers of each of the clutches and brakes to be linked without makingany complicated configuration of components.

The first forward speed is established by engaging the first clutch C-1and locking the second brake B-2; the second forward speed isestablished by engaging the first clutch C-1 and locking the first brakeB-1; the third forward speed is established by engaging the first clutchC-1 and the third clutch C-3; the fourth forward speed is established byengaging the first clutch C-1 and the fourth clutch C-4; the fifthforward speed is established by engaging the first clutch C-1 and thesecond clutch C-2; the sixth forward speed is established by engagingthe second clutch C-2 and the fourth clutch C-4; the seventh forwardspeed is established by engaging the second clutch C-2 and the thirdclutch C-3; the eighth forward speed is established by engaging thesecond clutch C-2 and locking the first brake B-1; and reverse speedsare established by engaging the third clutch C-3 or the fourth clutchC-4 and locking the second brake B-2.

In addition, in a velocity diagram in which the respective speeds of thesun gear S2, the sun gear S3, the carrier CR2, and the ring gear R3 ofthe planetary gear unit PU are shown on the ordinate, and thecorresponding gear ratios of the sun gear S2, the sun gear S3, thecarrier CR2, and the ring gear R3 are shown on the abscissa, the sungear S2 is positioned at the farthest left end of the ordinate and, insequence to the right thereof, are the carrier CR2, the ring gear R3that is linked to the counter gear 15, and the sun gear S3.

If the speed change mechanism 2 ₅ of the automatic transmission 1 ₅ ofthe fifth embodiment is rotated left-right 180° the result approximatesthe automatic transmission 1 ₁₀ of the tenth embodiment. However, in theautomatic transmission 1 ₁₀ according to the tenth embodiment, becausethe input rotation must be transferred to the fourth clutch C-4 throughthe inner circumferential side of the planetary gear unit PU, it is notpossible to separate the input shaft 12 and the intermediate shaft 13.

Sixth Embodiment

Next, a sixth embodiment, in which a portion of the first embodiment hasbeen modified, will be explained with reference to FIG. 11, which is across-sectional view of the automatic transmission 1 ₆ of the sixthembodiment. In describing the sixth embodiment below, those structuresthat are identical to those of the automatic transmission 1 ₁ of thefirst embodiment are denoted by identical reference numerals, anddescription thereof is omitted.

In the automatic transmission 1 ₆ of the sixth embodiment, the inputshaft 12 and the intermediate shaft 13 remain as in the firstembodiment, but the first through fourth clutches C-1 to C4, the firstand second brakes B-1 and B-2, the planetary gear set DP, the planetarygear unit PU, and the counter gear are bilaterally reversed, that is,the speed change mechanism 2 ₆ is rotated left-right 180°.

Thus, in the automatic transmission 1 ₆, the hydraulic servo 30 of thesecond clutch C-2 and the hydraulic servo 20 of the first clutch C-1 arelocated on the side of the planetary gear set DP that is axiallyopposite the planetary gear unit PU, the hydraulic servo 40 of the thirdclutch C-3 and the counter gear 15 are located axially intermediate theplanetary gear set DP and the planetary gear unit PU, and the hydraulicservo 50 of the fourth clutch C-4 and the hydraulic servo 60 of thefirst brake B-1 are located on the side of the planetary gear unit PUthat is axially opposite the planetary gear set DP.

In the automatic transmission 1 ₆, because the fourth clutch C-4 islocated in the transfer path to connect the input shaft 12 and the sungear S2, the second clutch C-2 is located in the transfer path toconnect the carrier CR1 and the carrier CR2, and the output sidetransfer member 103 of the second clutch C-2 is linked to the carrierCR2 on its side which faces at the planetary gear set DP, there is nomember enclosing the planetary gear unit PU, whereby the automatictransmission 1 ₆ is made more radially compact. In addition, it ispossible to shorten the transfer member that requires a high rigidity,and to thereby reduce the weight and to improve the controllability ofthe automatic transmission 1 ₆. Furthermore, the supplied lubricatingoil is readily discharged to those surfaces requiring lubrication. Inaddition, the assembly of the automatic transmission 1 ₆ can besimplified. Furthermore, because the structure includes a support wall120 and the working oil for the clutches can be supplied from thissupport wall due to the configuration of the clutches, it is possible toreduce the number of seal rings, to reduce the sliding resistance of theseal rings, and to improve the power transfer efficiency of theautomatic transmission 1 ₆.

The output side member 101 of the third clutch C-3, the output sidemember 102 of the first clutch C-1, and the output side transfer member103 of the second clutch C-2 are linked to the planetary gear unit PUthrough the inner circumferential side of the counter gear 15, making itis possible to locate the counter gear 15 axially intermediate theplanetary gear unit PU and the planetary gear set DP, and to use theautomatic transmission 1 ₆ in an FF-type vehicle.

Furthermore, because the hydraulic servo 30 of the second clutch C-2 islocated on the side of the planetary gear set DP that is axiallyopposite the planetary gear unit PU, it is possible to supply theworking oil to the hydraulic servo 30 of the second clutch C-2 from anoil duct provided in the boss 3 b. Thereby, in comparison to a structurein which the working oil is supplied from an oil duct in the input shaft12, it is possible to reduce the number of seal rings, to reduce thesliding resistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₆.

In addition, because the hydraulic servo 50 of the fourth clutch C-4 islocated on the side of the planetary gear unit PU that is axiallyopposite the planetary gear set DP, it is possible to locate thefriction plates 51 of the fourth clutch C-4 on the radially outer sideand to enlarge the surface area of the friction plates 51, and to thusensure transfer of a sufficient torque while reducing the number offriction plates 51. Furthermore, it is possible to supply working oil tothe hydraulic servo 50 of the fourth clutch C-4 from an oil duct c50 inthe boss 3 d. Whereby, in comparison to a structure in which the workingoil is supplied from an oil duct in the input shaft 12, it is possibleto reduce the number of seal rings, to reduce the sliding resistance ofthe seal rings, and to improve the power transfer efficiency of theautomatic transmission 1 ₆.

In addition, because the hydraulic servo 40 of the third clutch C-3 isaxially intermediate the planetary gear unit PU and the planetary gearset DP, in comparison to a structure in which the hydraulic servo 40 ofthe third clutch C-3 is located on the side of the planetary gear set DPthat is axially opposite the planetary gear unit PU, it is possible toshorten the distance between the third clutch C-3 and the planetary gearunit PU, and to shorten the output side transfer member 101 of the thirdclutch C-3, which must be strong in order to transfer high torque. It isthereby possible to reduce the weight and to improve the controllabilityof the automatic transmission 1 ₆.

Furthermore, because the hydraulic servo 20 of the first clutch C-1 islocated on the side of the planetary gear set DP that is axiallyopposite the planetary gear unit PU, it is possible to supply workingoil to the hydraulic servo 20 of the first clutch C-1 from an oil ductc20 in the boss 3 b. Thereby, in comparison to a structure in which, forexample, the hydraulic servo 20 of the first clutch C-1 is disposed onthe input shaft 12 and the working oil is supplied via the input shaft12, it is possible shorten the length of the oil duct and to improve thecontrollability of the automatic transmission 1 ₆.

Furthermore, because of provision of a first brake B-1 that selectivelylocks the sun gear S2 against rotation and because the hydraulic servo60 of the first brake B-1 is located on the side of planetary gear unitPU that is axially opposite the planetary gear set DP, the locking forcetransfer member of the first brake B-1 and the sun gear S2 can be linkedwithout making a complicated configuration, and the automatictransmission 1 ₆ can be made more compact.

In the automatic transmission 1 ₆, the transfer member 103 of the outputside of the second clutch C-2 extends axially around the outercircumferences of the transfer members 101, 102 to link with the carrierCR2, the transfer member 104 of the output side of the fourth clutch C-4and the transfer member 101 of the output side of third clutch C-3 arelinked to the sun gear S2, and the transfer member 104, the transfermember 101, and the sun gear S2, which rotate integrally, are located onthe radially inner side of the transfer member 103. Therefore, thetransfer member 104, which rotates faster than the transfer member 103,is further radially inward than the transfer member 102 of the outputside of the first clutch C-1, which is on the radially inner side of thetransfer member 103. Thus, it is possible to make the diameter of thetransfer member 104 smaller than the diameter of the transfer member 103and to reduce the weight as compared with a structure in which transfermember 104 is on the outer side. In addition, because the inertia isreduced as compared to a structure in which transfer member 104 isdisposed on the outer side, it is possible to improve thecontrollability of the automatic transmission 1 ₆.

The third and first clutches C-3, C-1 are located on the planetary gearset DP side, the transfer members 101, 102 are respectively linked tothe sun gear S2 and the sun gear S3, the fourth clutch C-4 is located onthe side of the planetary gear unit PU that is axially opposite theplanetary gear set DP, the transfer member 104 is linked to the sun gearS2, the second clutch C-2 is located on the planetary gear set DP side,and the transfer member 103 axially extends radially outward of members101, 102. Because the transfer member 104, which rotates faster than thetransfer member 103, is on the inner side, the diameter of the transfermember 104 can be made smaller than the diameter of the transfer member103, and it is possible to reduce the weight as compared to a structurein which transfer member 104 is disposed on the outer side. In addition,because it is possible to reduce the inertia as compared to that of astructure in which transfer member 104 is on the outside, it is possibleto improve the controllability of the automatic transmission 1 ₆.

In addition, in comparison to a structure in which the hydraulic servo50 of the fourth clutch C-4 is located between the planetary gear unitPU and the planetary gear set DP, it is possible to locate the frictionplates 51 of the fourth clutch C-4 more radially outward, and toincrease the area of the friction plates. Thus, it is possible to ensuretransfer of a sufficient torque while reducing the number of frictionplates 51. Furthermore, it is possible to shorten the distance betweenthe third and first clutches C-3, C-1 and the planetary gear unit PU,and it is possible to shorten the transfer members 101, 102 of theoutput sides of the third and first clutches C-3, C-1, which must bestrong in order to transfer a high torque. In this manner, it ispossible to decrease the weight and to improve the controllability ofthe automatic transmission 1 ₆.

Because the working oil is supplied to the hydraulic servo 50 of thefourth clutch C-4 from an oil duct c50 in the boss 3 b, in comparison toa structure in which the working oil is supplied from an oil duct in theinput shaft 12, it is possible to reduce the number of seal rings, toreduce the sliding resistance of the seal rings, and to improve thepower transfer efficiency of the automatic transmission 1 ₆.

In addition, because the transfer member of the input side of the fourthclutch C-4 is linked to the input shaft 12 and the intermediate shaft 13through the inner circumferential side of the planetary gear unit PU anda portion of the transfer member of the input side of the fourth clutchC-4 forms the clutch drum 52 of the hydraulic servo 50 of the fourthclutch C-4, as compared to a structure in which the transfer member ofthe output side of the fourth clutch C-4 forms the clutch drum of thehydraulic servo 50, in this embodiment the clutch drum of the hydraulicservo 50 can also serve to transfer power from the input shaft 12, andthus it is possible to form the transfer member more axially compact.

Furthermore, because the sun gear S1 is held stationary on boss 3 b,because the transfer member of the input side of the second clutch C-2is linked to the carrier CR1, because a portion of the transfer memberof the input side of the second clutch C-2 forms the clutch drum 32 ofthe hydraulic servo 30 of the second clutch C-2, and because thehydraulic servo 30 is located on the boss 3 b axially intermediate theplanetary gear set DP and the side wall 3 a, it is possible to supplythe working oil to the hydraulic servo 30 of the second clutch C-2 froman oil duct c30 in the boss 3 b. Thus, in comparison to a structure inwhich the hydraulic servo 30 of the second clutch C-2 is provided on theinput shaft 12 spaced from the boss 3 b and the working oil is suppliedvia an oil duct in the input shaft 12, it is possible to shorten thelength of the oil duct by an amount equivalent to the length of an oilduct in the input shaft 12, and it is possible to improve thecontrollability of the automatic transmission 1 ₆.

In addition, because the hub member 111 of the first clutch C-1 islinked to the ring gear R1, the transfer member 102 is linked to the sungear S3, a portion of the transfer member 102 forms the clutch drum 22of the hydraulic servo 20 of the first clutch C-1, and the hydraulicservo 20 is located on the boss 3 b axially intermediate the planetarygear set DP and the hydraulic servo 20 of the second clutch C-1, it ispossible to supply the working oil to the hydraulic servo 20 of thefirst clutch C-1 from an oil duct c20 in the boss 3 b. Thus, incomparison to a structure in which, for example, the hydraulic servo 20of the first clutch C-1 is disposed around the input shaft 12, separatedfrom the boss 3 b, and the working oil is supplied via an oil duct inthe input shaft 12, it is possible to shorten the length of the oil ductby an amount equivalent to the oil duct in the input shaft 12 that canbe eliminated, and it is possible to improve the controllability of theautomatic transmission 1 ₆.

Furthermore, because counter shaft 81 is arranged in parallel with theinput shaft 12 and is linked via the counter gear 15 to receive outputrotation from the ring gear R3, it is possible to advantageously use theautomatic transmission 1 ₆ in an FF-type vehicle.

In addition, because the counter gear 15 is located axially intermediatethe planetary gear unit PU and the planetary gear set DP and issupported by support member 120 a, it is possible to locate the countergear 15 closer to the input side, to position the counter shaft portion80 and the differential gear portion 90 on the torque converter side,and to thereby make the automatic transmission 1 ₆ more compact. Thus,it is possible to prevent interference between the transmission, thedifferential gear portion, etc. and the frame of the vehicle, and tofacilitate the mounting of the automatic transmission 1 ₆ in thevehicle.

Because the carrier CR1 is linked to the input shaft 12 on the sidefacing the planetary gear unit PU and is axially linked to the clutchdrum 32 on the side of the planetary gear set DP that is axiallyopposite the planetary gear unit PU, it is possible to link the carrierCR1, the transfer member 32 of the input side of the second clutch C-2,and the input shaft 12 without a complicated configuration and to makethe automatic transmission 1 ₆ more compact.

In addition, because the hub member 116 of the first brake B-1 and thetransfer member 104 that is linked thereto are axially linked to the sungear S2 on the side of the planetary gear unit PU that is axiallyopposite the planetary gear set DP, it is possible to link the hubmember 116 of the first brake B-1, the transfer member 104, and the sungear S2 without a complicated configuration and to make the automatictransmission 1 ₆ more compact.

In addition, because the planetary gear set DP includes the sun gear S1which is normally held stationary, a carrier CR1 that rotatably supportsthe pinion gear P1 and the pinion gear P2 and that is coupled to theoutput shaft 12, and a ring gear R1 that meshes with the pinion gear P2and outputs a reduced speed rotation, it is possible to output a reducedspeed rotation, i.e. at a speed less than that of the input rotation ofthe input shaft 12, from the ring gear R1.

Further, because the planetary gear unit PU is a Ravigneaux-typeplanetary gear unit PU that includes the sun gear S2, the sun gear S3,the short pinion P3 that meshes with the sun gear S3, the long pinion P4that meshes with the sun gear S2 and meshes with the short pinion P3,the carrier CR2 that rotatably supports the short pinion P3 and the longpinion P4, and the ring gear R3 that meshes with the long pinion P4, itis possible to prevent high speed rotation of the rotary elements and toprovide advantageous gear ratios while enabling each of the rotaryelements of the planetary gear unit PU and the output side members ofeach of the clutches and brakes to be linked without a complicatedconfiguration.

The first forward speed is established by engaging the first clutch C-1and locking the second brake B-2; the second forward speed isestablished by engaging the first clutch C-1 and locking the first brakeB-1; the third forward speed is established by engaging the first clutchC-1 and the third clutch C-3; the fourth forward speed is established byengaging the first clutch C-1 and the fourth clutch C-4; the fifthforward speed is established by engaging the first clutch C-1 and thesecond clutch C-2; the sixth forward speed is established by engagingthe second clutch C-2 and the fourth clutch C-4; the seventh forwardspeed is established by engaging the second clutch C-2 and the thirdclutch C-3; the eighth forward speed is established by engaging thesecond clutch C-2 and locking the first brake B-1; and reverse speedsare established by engaging the third clutch C-3 or the fourth clutchC-4 and locking the second brake B-2.

In a velocity diagram in which the respective speeds of the sun gear S2,the sun gear S3, the carrier CR2, and the ring gear R3 of the planetarygear unit PU are shown on the ordinate, and the corresponding gearratios of the sun gear S2, the sun gear S3, and carrier CR2, and thering gear R3 are shown on the abscissa, the sun gear S2 is positioned atthe farthest left end of the ordinate and, in sequence to the rightthereof, are the carrier CR2, the ring gear R3, and the sun gear S3.

Seventh Embodiment

Next, a seventh embodiment, in which a portion of the second embodimentdescribed above is modified, will be explained with reference to FIG. 12which is a cross-sectional view of an automatic transmission 1 ₇according to the second embodiment. In the description of the seventhembodiment which follows, the structures that are identical to those ofthe automatic transmission 1 ₂ according to the second embodiment aredenoted by identical reference numerals, and their description has beenomitted.

In the automatic transmission 1 ₇ of the seventh embodiment, the inputshaft 12 and the intermediate shaft 13 remain as in the secondembodiment, but the positions of the first through fourth clutches C-1to C-4, the first and second brakes B-1 to B-2, the planetary gear setDP, the planetary gear unit PU, and the counter gear 15 aresubstantially reversed, that is, the speed change mechanism 2 ₇ isrotated 180° left-right relative to the speed change mechanism 2 ₂ ofthe second embodiment.

Specifically, in the automatic transmission 1 ₇, the hydraulic servo 20of the first clutch C-1 is located on the side of the planetary gear setDP that is axially opposite the planetary gear unit PU. The hydraulicservo 40 of the third clutch C-3, the hydraulic servo 30 of the secondclutch C-2, and the counter gear 15 are located axially intermediate theplanetary gear set DP and the planetary gear unit PU, and the hydraulicservo 50 of the fourth clutch C-4 and the hydraulic servo 60 of thefirst brake B-1 are located on the side of the planetary gear unit PUthat is axially opposite the planetary gear set DP.

In this type of automatic transmission 1 ₇, because the fourth clutchC-4 is interposed in the transfer path to connect the input shaft 12 andthe sun gear S2, the second clutch C-2 is interposed in the transferpath to connect the carrier CR1 and the carrier CR2, and the output sidetransfer member 103 of the second clutch C-2 is linked to the side ofcarrier CR2 axially facing the planetary gear set DP, it is possible toavoid need for a member enclosing the planetary gear unit PU. Thereby,the automatic transmission 1 ₇ can be made more radially compact. Inaddition, it is possible to shorten the transfer member that requires ahigh rigidity, thereby reducing the weight and improving thecontrollability of the automatic transmission 1 ₇. Furthermore, thestructure permits lubricating oil to be readily discharged to structuresrequiring lubrication. In addition, the assembly of the automatictransmission 1 ₇ can be simplified. Furthermore, because the working oilfor the clutches can be supplied from support wall 120 due to theconfiguration of each of the clutches, it is possible to reduce thenumber of seal rings, to reduce the sliding resistance of the sealrings, and to improve the power transfer efficiency of the automatictransmission 1 ₇.

In addition, because the hydraulic servo 30 of the second clutch C-2 islocated axially intermediate the planetary gear unit PU and theplanetary gear set DP, it is possible to supply working oil to thehydraulic servo 30 of the second clutch C-2 from an oil duct in thesupport wall 120. Thereby, in comparison to a structure in which theworking oil is supplied from an oil duct in the input shaft 12, it ispossible to reduce the number of seal rings, to reduce the slidingresistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₇.

Furthermore, because the hydraulic servo 50 of the fourth clutch C4 islocated on the side of the planetary gear unit PU that is axiallyopposite the planetary gear set DP, it is possible to locate thefriction plates 51 of the fourth clutch C-4 more radially outward and toenlarge the surface area of the friction plates 51, and thus, it ispossible to ensure transfer of a sufficient torque, and to reduce thenumber of friction plates. Furthermore, it is possible to supply workingoil to the hydraulic servo 50 of the fourth clutch C-4 from an oil ductin the boss 3 d. Thereby, in comparison to a structure in which theworking oil is supplied from an oil duct in the input shaft 12, it ispossible to reduce the number of seal rings, to reduce the slidingresistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₇.

In addition, because the hydraulic servo 40 of the third clutch C-3 islocated axially intermediate the planetary gear unit PU and theplanetary gear set DP, in comparison to a structure in which thehydraulic servo 40 of the third clutch C-3 is located on the side of theplanetary gear set DP that is axially opposite the planetary gear unitPU, it is possible to shorten both the distance between the third clutchC-3 and the planetary gear unit PU and the output side transfer member101 of the third clutch C-3, which must be strong in order to transferhigh torque. Thereby, it is possible to reduce the weight and to improvethe controllability of the automatic transmission 1 ₇.

Furthermore, because the hydraulic servo 20 of the first clutch C-1 islocated on the side of the planetary gear set DP that is axiallyopposite the planetary gear unit PU, it is possible to supply workingoil to the hydraulic servo 20 of the first clutch C-1 from an oil ductin the boss 3 b. Thereby, in comparison to a structure in which workingoil is supplied from an oil duct in the input shaft 12, it is possibleto reduce the number of seal rings, to reduce the sliding resistance ofthe seal rings, and to improve the power transfer efficiency of theautomatic transmission 1 ₇.

In addition, because of provision of a first brake B-1 that selectivelylocks the sun gear S2 against rotation and because the hydraulic servo60 of the first brake B-1 is located on the side of planetary gear unitPU that is axially opposite the planetary gear set DP, the locking forcetransfer member of the first brake B-1 and the sun gear S2 can be linkedwithout making the these components complicated, and it is possible tomake the automatic transmission 1 ₇ more compact.

In the automatic transmission 1 ₇, the transfer member 103 of clutch C-2axially extends on the radially outer side of the transfer members 101,102, the transfer member 104 of the output side of the fourth clutch C-4and the transfer member 101 of the output side of third clutch C-3 arelinked to the sun gear S2, and the transfer member 104 of the outputside of the fourth clutch C-4, the transfer member 101 of the outputside of third clutch C-3, and the sun gear S2, which rotate integrally,are disposed on the inner side of the transfer member 102. Therefore,the transfer member 104, which rotates faster than the transfer member103, is located further toward the radially inner side than the transfermember 102, which is on the inner side of the transfer member 103. Thus,it is possible to make the diameter of the transfer member 104 smallerthan the diameter of the transfer member 103, and to reduce the weightmore than in a structure in which transfer member 104 is on the outerside. In addition, because the inertia is reduced in comparison to astructure in which transfer member 104 is located on the outer side, itis possible to improve the controllability of the automatic transmission1 ₇.

The third and first clutches C-3, C-1 are disposed on the side of theplanetary gear set that is axially opposite the planetary gear set DP,the transfer members 101, 102 are respectively linked to the sun gear S2and the sun gear S3, the fourth clutch C-4 is located on the side of theplanetary gear unit PU that is axially opposite the planetary gear setDP, the transfer member 104 is linked to the sun gear S2, the secondclutch C-2 is disposed on the side of the planetary gear set DP facingthe planetary unit PU, and the transfer member 103 links to the carrierCR2 by extending along the radially outer side of the transfer members101, 102. Thereby, because the transfer member 104, which rotates fasterthan the transfer member of the output side of the second clutch C-2, ismore radially inward, the diameter of the transfer member 104 of theoutput side of the fourth clutch C-4 can be made smaller than thediameter of the transfer member 103 of the output side of the secondclutch C-2, it is possible to reduce the weight as compared to astructure in which transfer member 103 is disposed on the outer side. Inaddition, because inertia is reduced the controllability of theautomatic transmission 1 ₇ is improved.

In addition, in comparison to a structure in which the hydraulic servo50 of the fourth clutch C-4 is located between the planetary gear unitPU and the planetary gear set DP, it is possible to locate the frictionplates 51 of the fourth clutch C-4 more radially outward and to increasethe area of the friction plates 51. Thus, transfer of a sufficienttorque is ensured, while enabling a reduction in the number of frictionplates 51. Furthermore, it is possible to shorten the distance betweenthe third and first clutches C-3, C-1 and the planetary gear unit PU,and to shorten the transfer members 101, 102, which must be strong inorder to transfer a high torque. Thus, it is possible to decreaseweight, and to improve the controllability of the automatic transmission1 ₇.

Furthermore, it is possible to supply the working oil to the hydraulicservo 50 of the fourth clutch CA from an oil duct c50 in the boss 3 b.Thereby, in comparison to a structure in which the working oil issupplied from an oil duct in the input shaft 12, it is possible toreduce the number of seal rings, to reduce the sliding resistance of theseal rings, and to improve the power transfer efficiency of theautomatic transmission 1 ₇.

In addition, because the transfer member of the input side of the fourthclutch C-4 is linked to the input shaft 12 and the intermediate shaft 13through the inner circumferential side of the planetary gear unit PU andbecause a portion of the transfer member of the input side of the fourthclutch C-4 serves as the clutch drum 52 of the hydraulic servo 50 of thefourth clutch C-4, in comparison to a structure in which the transfermember of the output side of the fourth clutch C-4 forms the clutch drum52, the clutch drum 52 of the hydraulic servo 50 can also serve totransfer power from the input shaft 12, and thus it is possible to formthe transfer member more axially compact.

Furthermore, because a counter gear 15 is linked to the ring gear R3 andis located axially intermediate the planetary gear unit PU and theplanetary gear set DP, because support member 120 a supports the countergear 15, because the hub member 112 of the second clutch C-2 links tothe carrier CR1 by axially extending on the outer side of the third andfirst clutches C-3, C-1, because a portion of the transfer member 103 ofthe output side of the second clutch C-2 forms the clutch drum 32 of thehydraulic servo 30 of the second clutch C-2, and because the hydraulicservo 30 is supported on the support member 120 a, between the planetarygear set DP and counter gear 15, it is possible to supply the workingoil to the hydraulic servo 30 of the second clutch C-2 from an oil ductc30 in the support member 120 a. Thus, in comparison to a structure inwhich the working oil is supplied from an oil duct in the input shaft12, it is possible to reduce the number of seal rings, to reduce thesliding friction of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₇.

In addition, because counter shaft 81 is arranged in parallel with theinput shaft 12 and linked via the counter gear 15 to the ring gear R3for receiving the output rotation, it is possible to advantageously usethe automatic transmission 1 ₇ in an FF-type vehicle.

Furthermore, because the counter gear 15 is located axially intermediatethe planetary gear unit PU and the planetary gear set DP and issupported by support member 120 a, it is possible to position thecounter gear 15 axially closer to the input side and to position thecounter shaft portion 80 and the differential gear portion 90 near thetorque converter 7, thereby making the automatic transmission 1 ₇ morecompact. Thus, interference between transmission, differential, etc. andthe frame is more easily avoided, and the mounting of the automatictransmission 1 ₇ in the vehicle is facilitated.

In addition, because the carrier CR1 is linked to the input shaft 12 onits side which faces the planetary gear unit PU and is linked to the hubmember 112 on the side of the planetary gear set DP that is axiallyopposite the planetary gear unit PU, it is possible to link the carrierCR1, the transfer member 112 of the input side of the second clutch C-2,and the input shaft 12 without making these members complicated, and itis possible to make the automatic transmission 1 ₇ more compact.

In addition, because the hub member 116 of the first brake B-1 and thetransfer member 104 are axially linked to the sun gear S2 on the side ofthe planetary gear unit PU that is axially opposite the planetary gearset DP, it is possible to link the hub member 116 of the first brakeB-1, the transfer member 104, and the sun gear S2 without making thesemembers complicated, and it is possible to make the automatictransmission 1 ₇ more compact.

In addition, because the planetary gear set DP includes the sun gear S1,which is normally held stationary, a carrier CR1 that rotatably supportsthe pinion gear P1 and the pinion gear P2 and that is linked to theoutput shaft 12, and a ring gear R1 that meshes with the pinion gear P2and outputs a reduced speed rotation, it is possible to output a reducedspeed rotation, i.e. rotation at a speed less than that of the inputrotation of the input shaft 12, from the ring gear R1.

In addition, because the planetary gear unit PU is a Ravigneaux-typeplanetary gear unit PU that includes the sun gear S2, the sun gear S3,the short pinion P3 that meshes with the sun gear S3, the long pinion P4that meshes with the sun gear S2 and with the short pinion P3, thecarrier CR2 that selectively rotatably supports the short pinion P3 andthe long pinion P4, and the ring gear R3 that meshes with the longpinion P4, it is possible to prevent high speed rotation of the rotaryelements and to provide advantageous gear ratios while enabling each ofthe rotary elements of the planetary gear unit PU and the output sidemembers of each of the clutches and brakes to be linked without makingthese members complicated.

The first forward speed is established by engaging the first clutch C-1and locking the second brake B-2; the second forward speed isestablished by engaging the first clutch C-1 and locking the first brakeB-1; the third forward speed is established by engaging the first clutchC-1 and the third clutch C-3; the fourth forward speed is established byengaging the first clutch C-1 and the fourth clutch C4; the fifthforward speed is established by engaging the first clutch C-1 and thesecond clutch C-2; the sixth forward speed is established by engagingthe second clutch C-2 and the fourth clutch C-4; the seventh forwardspeed is established by engaging the second clutch C-2 and the thirdclutch C-3; the eighth forward speed is established by engaging thesecond clutch C-2 and locking the first brake B-1; and reverse speedsare established by engaging the third clutch C-3 or the fourth clutchC-4 and locking the second brake B-2.

In addition, in a velocity diagram in which the respective speeds of thesun gear S2, the sun gear S3, the carrier CR2, and the ring gear R3 ofthe planetary gear unit PU are shown on the ordinate, and thecorresponding gear ratios of the sun gear S2, the sun gear S3, andcarrier CR2, and the ring gear R3 are shown on the abscissa, the sungear S2 is positioned at the farthest left end of the ordinate and,arrayed in sequence to the right thereof, are the carrier CR2, the ringgear R3 that is linked to the counter gear 15, and the sun gear S3.

Eighth Embodiment

Next, an eighth embodiment, in which a portion of the third embodimentis modified, will be explained with reference to FIG. 13 which is across-sectional view of an automatic transmission 1 ₈ according to theeighth embodiment. Note that in the description of the eighth embodimentwhich follows, structures that are identical to those of the automatictransmission 1 ₃ of the third embodiment are denoted by identicalreference numerals, and their description is omitted.

In the automatic transmission 1 ₈ of the eighth embodiment, the inputshaft 12 and the intermediate shaft 13 remain arranged as in thirdembodiment, and the arrangement of the first through fourth clutches C-1to C-4, the first and second brakes B-1 to B-2, the planetary gear setDP, the planetary gear unit PU, and the counter gear 15 aresubstantially reversed, that is, the speed change mechanism 2 ₈ isrotated left-right 180° as compared to the speed change mechanism 2 ₃.

The automatic transmission 1 ₈, the hydraulic servo 40 of the thirdclutch C-3, the hydraulic servo 20 of the first clutch C-1, thehydraulic servo 30 of the second clutch C-2, and the counter gear 15 arelocated axially intermediate the planetary gear set DP and the planetarygear unit PU, and the hydraulic servo 50 of the fourth clutch C-4 andthe hydraulic servo 60 of the first brake B-1 are located on the side ofthe planetary gear unit PU that is axially opposite the planetary gearset DP.

Because the fourth clutch C-4 is interposed in the transfer path toconnect the input shaft 12 and the sun gear S2, because the secondclutch C-2 is interposed in the transfer path to connect the carrier CR1and the carrier CR2, and because the output side transfer member 103 ofthe second clutch C-2 is linked to the side of carrier CR2 axiallyfacing the planetary gear set DP, it is possible to avoid need for amember enclosing the planetary gear unit PU. Thereby, the automatictransmission 1 ₈ can be made more radially compact. In addition, it ispossible to shorten the transfer member that requires a high rigidity,to reduce the weight, and to improve the controllability of theautomatic transmission 1 ₈. Furthermore, the structure allowslubricating oil to be readily discharged to structures requiringlubrication. In addition, the assembly of the automatic transmission 1 ₈for a vehicle is simplified. Furthermore, because working oil for theclutches is supplied from support wall 120, it is possible to reduce thenumber of seal rings, to reduce the sliding resistance of the sealrings, and to improve the power transfer efficiency of the automatictransmission 1 ₈.

In addition, because the hydraulic servo 30 of the second clutch C-2 islocated axially intermediate the planetary gear unit PU and theplanetary gear set DP, it is possible to supply working oil to thehydraulic servo 30 of the second clutch C-2 from an oil duct in thesupport wall 120. Thereby, as compared to a structure wherein theworking oil is supplied from an oil duct in the input shaft 12, it ispossible to reduce the number of seal rings, to reduce the slidingresistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₈.

Furthermore, because the hydraulic servo 50 of the fourth clutch C-4 islocated on the side of the planetary gear unit PU that is axiallyopposite the planetary gear set DP, it is possible to locate thefriction plates 51 of the fourth clutch C-4 more radially outward and toenlarge the surface area of the friction plates 51, and thus, it ispossible to transfer sufficient torque while reducing the number offriction plates. Furthermore, because working oil is supplied to thehydraulic servo 50 of the fourth clutch C-4 from an oil duct in the boss3 d, in comparison to a structure in which the working oil is suppliedfrom an oil duct in the input shaft 12, it is possible to reduce thenumber of seal rings, to reduce the sliding resistance of the sealrings, and to improve the power transfer efficiency of the automatictransmission 1 ₈.

In addition, because the hydraulic servo 40 of the third clutch C-3 islocated axially intermediate the planetary gear unit PU and theplanetary gear set DP, as compared to a structure in which the hydraulicservo 40 of the third clutch C-3 is located on the side of the planetarygear set DP that is axially opposite the planetary gear unit PU, it ispossible to shorten the distance between the third clutch C-3 and theplanetary gear unit PU, and to shorten the output side transfer member101 of the third clutch C-3, which must be strong in order to transferhigh torque. It is thereby possible to reduce the weight and to improvethe controllability of the automatic transmission 1 ₂.

Furthermore, because the hydraulic servo 20 of the first clutch C-1 islocated axially intermediate the planetary gear unit PU and theplanetary gear set DP, as compared to a structure in which the hydraulicservo 20 of the first clutch C-1 is located on the side of the planetarygear set DP that is axially opposite the planetary gear unit PU, it ispossible to shorten the distance between the first clutch C-1 and theplanetary gear unit PU, and to shorten the output side transfer member102 of the first clutch C-1, which must be strong in order to transferhigh torque. It is thereby possible to reduce the weight, and to improvethe controllability of the automatic transmission 1 ₈.

In addition, because a first brake B-1 selectively locks the rotation ofthe sun gear S2 and the hydraulic servo 60 of the first brake B-1 islocated on the side of planetary gear unit PU that is axially oppositethe planetary gear set DP, the locking force transfer member of thefirst brake B-1 and the sun gear S2 can be linked without making thesemembers complicated, and it is possible to make the automatictransmission 1 ₈ more compact.

In the automatic transmission 1 ₈, the transfer member 103 of the outputside of the second clutch C-2, which is linked to the carrier CR2,extends axially on the radially outer side of the transfer members 101,102, the transfer member 104 and the transfer member 101 are linked tothe sun gear S2, and the transfer member 104, the transfer member 101,and the sun gear S2, which rotate integrally, are arranged radiallyinward of the transfer member 102. Therefore, the transfer member 104 ofthe output side of the fourth clutch C-4, which rotates faster than thetransfer member 103, is more radially inward than the transfer member102, which is on the inner side of the transfer member 103. Thus, it ispossible to make the diameter of the transfer member 104 smaller thanthe diameter of the transfer member 103, and to reduce weight ascompared with a structure in which transfer member 104 is on the outercircumferential side. In addition, because the inertia is reduced incomparison to a structure in which the transfer member is located on theradially outer side, it is possible to improve the controllability ofthe automatic transmission 1 ₈.

The third and first clutches C-3, C-1 are located on the side of theplanetary gear set DP, the transfer members 101, 102 are respectivelylinked to the sun gear S2 and the sun gear S3, the fourth clutch C4 islocated on the side of the planetary gear unit PU that is axiallyopposite the planetary gear set DP, the transfer member 104 of theoutput side of the fourth clutch C4 is linked to the sun gear S2, thesecond clutch C-2 is located on the side of the planetary gear set DP,and the transfer member 103 extends axially on the radially outer sideof the transfer members 101, 102 to link to the carrier CR2. Thus,because the transfer member 104, which rotates faster than the transfermember of the output side of the second clutch C-2, is on the radiallyinner side, the diameter of the transfer member 104 can be made smallerthan the diameter of the transfer member 103 thus reducing weight ascompared to a structure in which the transfer member 104 is located onthe outer side. In addition, because the inertia is thereby reduced, itis possible to improve the controllability of the automatic transmission1 ₈.

In comparison to a structure in which the hydraulic servo 50 of thefourth clutch C-4 is located between the planetary gear unit PU and theplanetary gear set DP, it is possible to locate the friction plates ofthe fourth clutch C-4 more radially outward, and to increase the area ofthe friction plates 51. Thus, it is possible to ensure transfer of asufficient torque, while reducing the number of friction plates 51.Furthermore, it is possible to shorten the distance between the thirdand first clutches C-3, C-1 and the planetary gear unit PU, and toshorten the transfer members 101, 102, which must be strong in order totransfer a high torque. Weight is thereby decreased, and thecontrollability of the automatic transmission 1 ₈ is improved.

The working oil is supplied to the hydraulic servo 50 of the fourthclutch C4 from an oil duct c50 in the boss 3 b. Thereby, in comparisonto a structure in which the working oil is supplied from an oil duct inthe input shaft 12, it is possible to reduce the number of seal rings,to reduce the sliding resistance of the seal rings, and to improve thepower transfer efficiency of the automatic transmission 1 ₈.

In addition, because the transfer member of the input side of the fourthclutch C-4 is linked to the input shaft 12 and the intermediate shaft 13by extending through the inner circumferential side of the planetarygear unit PU and a portion of the transfer member of the input side ofthe fourth clutch C-4 forms the clutch drum 52 of the hydraulic servo 50of the fourth clutch C-4, as contrasted with a structure in which thetransfer member of the output side of the fourth clutch C-4 forms theclutch drum of the hydraulic servo 50, the clutch drum of the hydraulicservo 50 can also serve to transfer power from the input shaft 12, andthus it is possible to form the transfer member more axially compact.

Furthermore, because counter gear 15 is linked to the ring gear R3 andis located axially intermediate the planetary gear unit PU and theplanetary gear set DP, because a support wall 120 a supports the countergear 15, because the hub 112 of the second clutch C-2 extends around theouter circumferences of the third and first clutches C-3, C-1 to linkwith the carrier CR1, because a portion of the transfer member 103 ofthe output side of the second clutch C-2 forms the clutch drum 32 of thehydraulic servo 30 of the second clutch C-2, and because the hydraulicservo 30 is located on the support member 120 a, between the planetarygear set DP and counter gear 15, it is possible to supply the workingoil to the hydraulic servo 30 of the second clutch C-2 from an oil ductc30 in the support member 120 a. Thus, in comparison to a structure inwhich the working oil is supplied from an oil duct in the input shaft12, it is possible to reduce the number of seal rings, to reduce thesliding friction of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₈.

Furthermore, because the transfer member 102 of the output side of thefirst clutch C-1 is linked to the sun gear S3, because a portion of thetransfer member 102 of the output side of the first clutch C-1 forms theclutch drum 22 of the hydraulic servo 20 of the first clutch C-1,because the hydraulic servo 20 is mounted on the support member 120 aaxially intermediate the planetary gear set DP and the hydraulic servo30 of the second clutch C-2, because the transfer member 101 of theoutput side of the third clutch C-3 is linked to the sun gear S2,because a portion of the transfer member 101 forms the drum clutch 42 ofthe hydraulic servo 40 of the third clutch C-3, and because thehydraulic servo 40 is located axially intermediate the planetary gearset DP and the hydraulic servo 20 of the first clutch C-1, it ispossible to provide the working oil to the hydraulic servo 20 of thefirst clutch C-1 from an oil duct c20 that extends through the supportwall 120 and the support member 120 a. Thus, in comparison to astructure in which the working oil is supplied from an oil duct in theinput shaft 12, it is possible to reduce the number of seal rings, toreduce the sliding resistance of the seal rings, and to improve thepower transfer efficiency of the automatic transmission 1 ₈. Inaddition, because the hydraulic servo 40 of the third clutch C-3 islocated axially intermediate the planetary gear unit PU and theplanetary gear set DP, in comparison to a structure in which thehydraulic servo 40 of the third clutch C-3 is located on the side of theplanetary gear set DP that is axially opposite the planetary gear unitPU, it is possible to shorten the distance between the third clutch C-3and the planetary gear unit PU, and to shorten the transfer member 101,which must be strong in order to transfer a high torque. It is therebypossible to reduce the weight and to improve the controllability of theautomatic transmission.

Because counter shaft 81 is arranged in parallel with the input shaft 12and linked via the counter gear 15 for receipt of output rotation fromthe ring gear R3, it is possible to advantageously use the automatictransmission 1 ₈ in an FF-type vehicle.

Furthermore, because the counter gear 15 is located axially intermediatethe planetary gear unit PU and the planetary gear set DP and issupported on a support member 120 a, it is possible to position thecounter gear 15 axially closer to the input side, to position thecounter shaft portion 80 and the differential gear portion 90 near thetorque converter 7, and to thereby make the automatic transmission 1 ₈more compact. Accordingly, it is possible to prevent interferencebetween the transmission, differential, etc. and the frame, and tofacilitate the mounting of the automatic transmission 1 ₈ in thevehicle.

In addition, because the carrier CR1 is linked to the input shaft 12 onits side facing the planetary gear unit PU and is linked to the hubmember 112, which is the transfer member of the input side of the secondclutch C-2, on its side axially opposite the planetary gear unit PU, itis possible to link the carrier CR1, the transfer member 112 of theinput side of the second clutch C-2, and the input shaft 12 withoutmaking these members complicated, and to make the automatic transmission1 ₈ more compact.

In addition, because the hub member 116 of the first brake B-1 and thetransfer member 104 that is linked thereto are axially linked to the sungear S2 on the side of the planetary gear unit PU that is opposite theplanetary gear set DP, it is possible to link the hub member 116 of thefirst brake B-1, the transfer member 104, and the sun gear S2 without acomplicated configuration, and to make the automatic transmission 1 ₈more compact.

In addition, because the planetary gear set DP includes the sun gear S1which is non-rotatably mounted on the case 4, a carrier CR1 thatrotatably supports the pinion gear P1 and the pinion gear P2 and that isconnected to the output shaft 12, and a ring gear R1 that meshes withthe pinion gear P2 and that outputs a reduced speed rotation, it ispossible to output a reduced speed rotation, i.e. at a speed less thanthat of the input rotation of the input shaft 12, from the ring gear R1.

In addition, because the planetary gear unit PU is a Ravigneaux-typeplanetary gear unit PU that includes the sun gear S2, the sun gear S3,the short pinion P3 that meshes with the sun gear S3, the long pinion P4that meshes with the sun gear S2 and with the short pinion P3, thecarrier CR2 that rotatably supports the short pinion P3 and the longpinion P4, and the ring gear R3 that meshes with the long pinion P4, itis possible to prevent high speed rotation of each of the rotaryelements and to provide advantageous gear ratios while enabling each ofthe rotary elements of the planetary gear unit PU and the output sidemembers of each of the clutches and brakes to be linked without acomplicated configuration.

The first forward speed is established by engaging the first clutch C-1and locking the second brake B-2; the second forward speed isestablished by engaging the first clutch C-1 and locking the first brakeB-1; the third forward speed is established by engaging the first clutchC-1 and the third clutch C-3; the fourth forward speed is established byengaging the first clutch C-1 and the fourth clutch C-4; the fifthforward speed is established by engaging the first clutch C-1 and thesecond clutch C-2; the sixth forward speed is established by engagingthe second clutch C-2 and the fourth clutch C-4; the seventh forwardspeed is established by engaging the second clutch C-2 and the thirdclutch C-3; the eighth forward speed is established by engaging thesecond clutch C-2 and locking the first brake B-1; and reverse speedsare established by engaging the third clutch C-3 or the fourth clutchC-4 and locking the second brake B-2.

In a velocity diagram in which the respective speeds of the sun gear S2,the sun gear S3, the carrier CR2, and the ring gear R3 of the planetarygear unit PU are shown on the ordinate, and the corresponding gearratios of the sun gear S2, the sun gear S3, and carrier CR2, and thering gear R3 are shown on the abscissa, the sun gear S2 is positioned atthe farthest left end on the ordinate and, in sequence to the rightthereof, are the carrier CR2, the ring gear R3 that is linked to thecounter gear 15, and the sun gear S3.

Ninth Embodiment

Next, a ninth embodiment, in which a portion of the fourth embodiment ismodified, will be explained with reference to FIG. 14 which is across-sectional view of an automatic transmission 1 ₉ according to theninth embodiment. In the description of the ninth embodiment, structuresthat are identical to those of the automatic transmission 1 ₄ accordingto the fourth embodiment are denoted by identical reference numerals,and their description has been omitted.

In the automatic transmission 1 ₉ according to the ninth embodiment, theinput shaft 12 and the intermediate shaft 13 and the engine retain thesame arrangement. However, the relative disposition of the first throughfourth clutches C-1 to C-4, the first and second brakes B-1 and B-2, theplanetary gear set DP, the planetary gear unit PU, and the counter gear15 are substantially reversed, that is, the speed change mechanism 2 ₉is substantially obtained by rotating the speed change mechanism 2 ₄ ofthe fourth embodiment left-right 180°.

Specifically, in the automatic transmission 1 ₉, the hydraulic servo 40of the third clutch C-3 is located on the side of the planetary gear setDP that is axially opposite the planetary gear unit PU, the hydraulicservo 20 of the first clutch C-1, the hydraulic servo 30 of the secondclutch C-2, and the counter gear 15 are located axially intermediate theplanetary gear set DP and the planetary gear unit PU, and the hydraulicservo 50 of the fourth clutch C-4 and the hydraulic servo 60 of thefirst brake B-1 are located on the side of the planetary gear unit PUthat is axially opposite the planetary gear set DP.

Because the fourth clutch C-4 is interposed in the transfer path toconnect the input shaft 12 and the sun gear S2, the second clutch C-2 isinterposed in the transfer path to connect the carrier CR1 and thecarrier CR2, and the output side transfer member 103 of the secondclutch C-2 is linked to the side of the carrier CR2 facing the planetarygear set DP, it is possible to avoid provision of a member enclosing theplanetary gear unit PU. The automatic transmission 1 ₉ can thereby bemade more radially compact. In addition, it is possible to shorten thetransfer member that requires a high rigidity, to reduce the weight, andto improve the controllability of the automatic transmission 1 ₉.Furthermore, this structure allows lubricating oil to be readilydischarged where needed, and cooling performance can be ensured. Inaddition, the assembly of the automatic transmission 1 ₉ is simplified.Furthermore, because the working oil for the clutches can be suppliedfrom support wall 120 due to the configuration of each of the clutches,it is possible to reduce the number of seal rings, to reduce the slidingresistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₉.

Because the hydraulic servo 30 of the second clutch C-2 is locatedaxially intermediate the planetary gear unit PU and the planetary gearset DP, it is possible to supply working oil to the hydraulic servo 30of the second clutch C-2 from an oil duct provided in the support wall120. Thereby, in comparison to a structure in which the working oil issupplied from an oil duct in the input shaft 12, it is possible toreduce the number of seal rings, to reduce the sliding resistance of theseal rings, and to improve the power transfer efficiency of theautomatic transmission 1 ₉.

Furthermore, because the hydraulic servo 50 of the fourth clutch C4 islocated on the side of the planetary gear unit PU that is axiallyopposite the planetary gear set DP, it is possible to locate thefriction plates 51 of the fourth clutch C-4 more radially outward and toenlarge the surface area of the friction plates 51, and thus, it ispossible to transfer sufficient torque while reducing the number offriction plates. Working oil is supplied to the hydraulic servo 50 ofthe fourth clutch C-4 from an oil duct in the boss 3 d. Thereby, incomparison to a structure in which the working oil is supplied from anoil duct in the input shaft 12, it is possible to reduce the number ofseal rings, to reduce the sliding resistance of the seal rings, and toimprove the power transfer efficiency of the automatic transmission 1 ₉.

Because the hydraulic servo 40 of the third clutch C-3 is located on theside of the planetary gear set DP that is axially opposite the planetarygear unit PU, it is possible to supply the working oil to the hydraulicservo 40 of the third clutch C-3 from an oil duct in the boss 3 b.Thereby, in comparison to a structure in which the working oil issupplied from an oil duct in the input shaft 12, it is possible toreduce the number of seal rings, to reduce the sliding resistance of theseal rings, and to improve the power transfer efficiency of an automatictransmission 1 ₉.

Furthermore, because the hydraulic servo 20 of the first clutch C-1 islocated axially intermediate the planetary gear unit PU and theplanetary gear set DP, in comparison to a structure in which thehydraulic servo 20 of the first clutch C-1 is located on the side of theplanetary gear set DP that is axially opposite the planetary gear unitPU, it is possible to shorten the distance between the first clutch C-1and the planetary gear unit PU, and to thereby shorten the output sidetransfer member 102 of the first clutch C-1, which requires strength inorder to transfer a high torque. Thereby, it is possible to reduce theweight and to improve the controllability of the automatic transmission1 ₉.

First brake B-1 selectively locks the sun gear S2 to the case 4 therebypreventing rotation. Because the hydraulic servo 60 of the first brakeB-1 is located on the side of planetary gear unit PU that is axiallyopposite the planetary gear set DP, the locking force transfer member ofthe first brake B-1 and the sun gear S2 can be linked without makingthese members complicated, and it is possible to make the automatictransmission 1 ₉ more compact.

In the automatic transmission 1 ₉, the transfer member 103 of the outputside of the second clutch C-2, which is linked to the carrier CR2,extends along the outer circumferential side of the transfer members101, 102 of the output side of the third and first clutches C-3, C-1,the transfer member 104 of the output side of the fourth clutch C4 andthe transfer member 101 of the output side of third clutch C-3 arelinked to the sun gear S2, and the transfer member 104 of the outputside of the fourth clutch C-4, the transfer member 101 of the outputside of third clutch C-3, and the sun gear S2, which rotate integrally,are located on the inner circumferential side of the transfer member102. Therefore, the transfer member 104, which rotates faster than thetransfer member 103, is positioned more radially inward than is thetransfer member 102 of the output side of the first clutch C-1, which ison the inner circumferential side of the transfer member 103 of theoutput side of the second clutch C-2. Thus, it is possible to make thediameter of the transfer member 104 smaller than the diameter of thetransfer member 103, and to reduce the weight as compared to a structurein which the transfer member 104 is on the outer circumferential side oftransfer member 102. In addition, because the inertia is reduced incomparison to a structure in which transfer member 104 is disposed onthe outer circumferential side of transfer member 102, it is possible toimprove the controllability of the automatic transmission 1 ₉.

In addition, the third and first clutches C-3, C-1 are disposed on theplanetary gear set DP side, the transfer members 101, 102 arerespectively linked to the sun gear S2 and the sun gear S3, the fourthclutch C4 is located on the side of the planetary gear unit PU that isaxially opposite the planetary gear set DP, the transfer member 104 islinked to the sun gear S2, the second clutch C-2 is located on theplanetary gear set DP side, and the transfer member 103 which is linkedto the carrier CR2 is coaxial with and radially outward of the transfermembers 101, 102. Thereby, because the transfer member 104, whichrotates faster than the transfer member of the output side of the secondclutch C-2, is more radially inward, its diameter can be made smallerthan the diameter of the transfer member 103, and it is possible toreduce the weight as compared to a structure in which transfer member104 is located on the outer circumferential side of transfer members101,102. In addition, because the inertia is reduced in comparison to astructure in which transfer member 104 is on the outside, it is possibleto improve the controllability of the automatic transmission 1 ₉.

In addition, in comparison to a structure in which the hydraulic servo50 of the fourth clutch C-4 is located between the planetary gear unitPU and the planetary gear set DP, it is possible to locate the frictionplates 51 of the fourth clutch C-4 more radially outward, and to enlargethe area of the friction plates. Thus, it is possible to transfersufficient torque while reducing the number of friction plates 51.Furthermore, it is possible to shorten the distance between the thirdand first clutches C-3, C-1 and the planetary gear unit PU, and tothereby shorten the transfer members 101, 102, which must be strong inorder to transfer a high torque. It is thereby possible to decrease theweight, and to improve the controllability of the automatic transmission1 ₉.

Working oil is supplied to the hydraulic servo 50 of the fourth clutchC-4 from an oil duct c50 in the boss 3 b. Thereby, in comparison to astructure in which working oil is supplied from an oil duct in the inputshaft 12, it is possible to reduce the number of seal rings, to reducethe sliding resistance of the seal rings, and to improve the powertransfer efficiency of the automatic transmission 1 ₉.

A portion of the transfer member of the input side of the fourth clutchC-4 forms the clutch drum 52 of the hydraulic servo 50 of the fourthclutch C-4. Accordingly, compared to a structure in which the transfermember of the output side of the fourth clutch C-4 forms the clutch drumof the hydraulic servo 50, the clutch drum of the hydraulic servo 50 canalso serve to transfer power from the input shaft 12, and thus it ispossible to form the transfer member more axially compact.

Furthermore, because counter gear 15 is linked to the ring gear R3 andis located axially intermediate the planetary gear unit PU and theplanetary gear set DP, because support member 120 a supports the countergear 15, because the hub 112 of the second clutch C-2 links to thecarrier CR1 by extending around the outer circumference of the third andfirst clutches C-3, C-1, because a portion of the transfer member 103forms the clutch drum 32 of the hydraulic servo 30 of the second clutchC-2, and because the hydraulic servo 30 is mounted on the support member120 a between the planetary gear set DP and counter gear 15, it ispossible to supply the working oil to the hydraulic servo 30 of thesecond clutch C-2 from an oil duct c30 in the support member 120 a.Thus, in comparison to a structure in which the working oil is suppliedfrom an oil duct in the input shaft 12, it is possible to reduce thenumber of seal rings, to reduce the sliding friction of the seal rings,and to improve the power transfer efficiency of the automatictransmission 1 ₉.

Boss 3 b which extends from the side wall 3 a of the case 4 supports thesun gear S1 and fixes it against rotation, the transfer member of theinput side of the third clutch C-3 is linked to the ring gear R1 and aportion thereof forms the clutch drum 42 of the hydraulic servo 40 ofthe third clutch C-3. The hydraulic servo 40 is mounted on the boss 3 baxially intermediate the planetary gear set DP and the side wall 3 a.The transfer member of the input side of the first clutch C-1 is linkedto the transfer member of the input side of the third clutch C-3, and aportion of the transfer member of the input side of the first clutch C-1forms the clutch drum 22 of the hydraulic servo 20 of the first clutchC-1. The hydraulic servo 20 is mounted on the support member 120 aaxially intermediate the planetary gear set DP and the hydraulic servo30 of the second clutch C-2. Accordingly, it is possible to supply theworking oil to the hydraulic servo 40 of the third clutch C-3 from anoil duct c40 in the boss 3 b. Thus, in comparison to a structure inwhich the hydraulic servo 40 of the third clutch C-3 is disposed on theinput shaft 12 and spaced from the boss 3 b and in which the working oilis supplied via an oil duct in the input shaft 12, it is possible toshorten the length of the oil duct by an amount equivalent to the lengthof an oil duct in the input shaft 12, and to improve the controllabilityof the automatic transmission 1 ₉. In addition, it is possible to supplythe working oil to the hydraulic servo 20 of the first clutch C-1 froman oil duct c20 which extends through the support wall 120 and thesupport member 120 a. Thus, in comparison to a structure in which theworking oil is supplied from an oil duct in the input shaft 12, it ispossible to reduce the number of seal rings, to reduce the slidingresistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₉.

In addition, because counter shaft 81 is arranged in parallel with theinput shaft 12 and linked via the counter gear 15 to the ring gear R3 soas to receive the output rotation from the ring gear R3, it is possibleto advantageously use the automatic transmission 1 ₉ in an FF-typevehicle.

Furthermore, because the counter gear 15 is located axially intermediatethe planetary gear unit PU and the planetary gear set DP and issupported by a support member 120 a, it is possible to position thecounter gear 15 axially closer to the input side, to position thecounter shaft portion 80 and the differential gear portion 90 near thetorque converter 7, and to make the automatic transmission 1 ₉ morecompact. It is thereby possible to prevent interference betweentransmission, differential, etc. and the frame of the vehicle, and tofacilitate the mounting of the automatic transmission 1 ₉ in thevehicle.

In addition, because the carrier CR1 is linked to the input shaft 12 onthe planetary gear unit PU side and is axially linked to the hub member112, which is the transfer member of the input side of the second clutchC-2, at the side of the planetary gear set DP that is axially oppositethe planetary gear unit PU, it is possible to link the carrier CR1, thetransfer member 112, and the input shaft 12 without making these memberscomplicated, and it is possible to make the automatic transmission 1 ₉more compact.

In addition, because the hub member 116 of the first brake B-1 and thetransfer member 104 that is linked thereto are axially linked to the sungear S2 on the side of the planetary gear unit PU that is axiallyopposite the planetary gear set DP, it is possible to link the hubmember 116 of the first brake B-1, the transfer member 104, and the sungear S2 without making these members complicated and to thereof make theautomatic transmission 1 ₉ more compact.

In addition, because the planetary gear set DP includes the non-rotarysun gear S1, a carrier CR1 that rotatably supports the pinion gear P1and the pinion gear P2 and that is linked to the output shaft 12, and aring gear R1 that meshes with the pinion gear P2 and outputs a reducedspeed rotation, it is possible to output a reduced speed rotation, i.e.at a speed that is less than that of the input rotation of the inputshaft 12, from the ring gear R1.

In addition, because the planetary gear unit PU is a Ravigneaux-typeplanetary gear unit PU that includes the sun gear S2, the sun gear S3,the short pinion P3 that meshes with the sun gear S3, the long pinion P4that meshes with the sun gear S2 and with the short pinion P3, thecarrier CR2 that selectively rotatably supports the short pinion P3 andthe long pinion P4, and the ring gear R3 that meshes with the longpinion P4, it is possible to prevent high speed rotation of each of therotary elements and to provide advantageous gear ratios while enablingeach of the rotary elements of the planetary gear unit PU and the outputside members of each of the clutches and brakes to be linked withoutmaking these members complicated.

The first forward speed is established by engaging the first clutch C-1and locking the second brake B-2; the second forward speed isestablished by engaging the first clutch C-1 and locking the first brakeB-1; the third forward speed is established by engaging the first clutchC-1 and the third clutch C-3; the fourth forward speed is established byengaging the first clutch C-1 and the fourth clutch C-4; the fifthforward speed is established by engaging the first clutch C-1 and thesecond clutch C-2; the sixth forward speed is established by engagingthe second clutch C-2 and the fourth clutch C4; the seventh forwardspeed is established by engaging the second clutch C-2 and the thirdclutch C-3; the eighth forward speed is established by engaging thesecond clutch C-2 and locking the first brake B-1; and reverse speedsare established by engaging the third clutch C-3 or the fourth clutch C4and locking the second brake B-2.

In a velocity diagram in which the respective speeds of the sun gear S2,the sun gear S3, the carrier CR2, and the ring gear R3 of the planetarygear unit PU are shown on the ordinate, and the corresponding gearratios of the sun gear S2, the sun gear S3, and carrier CR2, and thering gear R3 are shown on the abscissa, a structure becomes possible inwhich the sun gear S2 is positioned at the farthest left end of theordinate and, in sequence to the right thereof, are the carrier CR2, thering gear R3 that is linked to the counter gear 15, and the sun gear S3.

Tenth Embodiment

Next, a tenth embodiment, in which a portion of the fifth embodiment ismodified, will be explained with reference to FIG. 15 which is across-sectional view of an automatic transmission 1 ₁₀ according to thetenth embodiment. In the description of the tenth embodiment below, thestructures that are identical to those of the automatic transmission 1 ₅according to the fifth embodiment are denoted by identical referencenumerals, and their description is omitted.

In the automatic transmission 1 ₁₀ according to a tenth embodiment thegeneral arrangement of the input shaft 12, the intermediate shaft 13 andthe engine is retained. However, the disposition of the first to fourthclutches C-1 to C-4, the first and second brakes B-1 and B-2, theone-way clutch F-1, the planetary gear set DP, the planetary gear unitPU, and the counter gear 15 is substantially reversed, that is, thespeed change mechanism 2 ₁₀ is similar to the speed change mechanism 2 ₅rotated left-right 180°.

Specifically, in the automatic transmission 1 ₁₀, the hydraulic servo 40of the third clutch C-3 is located on the side of the planetary gear setDP that is axially opposite the planetary gear unit PU. The hydraulicservo 50 of the fourth clutch C-4, the hydraulic servo 20 of the firstclutch C-1, the hydraulic servo 30 of the second clutch C-2, and thecounter gear 15 are located axially intermediate the planetary gear setDP and the planetary gear unit PU, and the hydraulic servo 60 of thefirst brake B-1 is located on the side of the planetary gear unit PUthat is axially opposite the planetary gear set DP.

In the automatic transmission 1 ₁₀ of the tenth embodiment, because itis necessary to transfer the input rotation to the fourth clutch C-4through the inner circumferential side of the planetary gear unit PU, itis not possible to separate the input shaft 12 from the intermediateshaft 13. Accordingly, in this embodiment, the input shaft 12 and theintermediate shaft 13 are splined together.

In the automatic transmission 1 ₁₀, because the fourth clutch C-4 isinterposed in the transfer path to connect the input shaft 12 and thesun gear S2, the second clutch C-2 is interposed in the transfer path toconnect the carrier CR1 and the carrier CR2, and the output sidetransfer member 103 of the second clutch C-2 is linked to the side ofthe carrier CR2 facing the planetary gear set DP, it is possible toavoid inclusion of a member enclosing the planetary gear unit PU.Thereby, the automatic transmission 1 ₁₀ can be made more radiallycompact. In addition, it is possible to shorten the transfer member thatrequires a high rigidity, to reduce the weight, and to improve thecontrollability of the automatic transmission 1 ₁₀. Furthermore, thestructure allows lubricating oil to be readily discharged where neededto ensure cooling performance. In addition, the assembly of theautomatic transmission 1 ₁₀ is simplified. Furthermore, because theworking oil for the clutches is supplied from support wall 120, due tothe configuration of each of the clutches, it is possible to reduce thenumber of seal rings, to reduce the sliding resistance of the sealrings, and to improve the power transfer efficiency of the automatictransmission 1 ₁₀.

In addition, because the hydraulic servo 30 of the second clutch C-2 islocated axially intermediate the planetary gear unit PU and theplanetary gear set DP, it is possible to supply working oil to thehydraulic servo 30 of the second clutch C-2 from an oil duct provided inthe support wall 120. Thereby, in comparison to a structure in which theworking oil is supplied from an oil duct in the input shaft 12, it ispossible to reduce the number of seal rings, to reduce the slidingresistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₁₀.

In addition, because the hydraulic servo 50 of the fourth clutch C-4 islocated axially intermediate the planetary gear unit PU and theplanetary gear set DP and adjacent to the planetary gear set DP, it ispossible for portions of the carrier CR1 and the clutch drum 52 to beshared in common (that is, the clutch drum 52 and the side plate of thecarrier CR1), and to thereby reduce the weight and size.

Furthermore, because the hydraulic servo 40 of the third clutch C-3 islocated on the side of the planetary gear set DP that is axiallyopposite the planetary gear unit PU, it is possible to supply theworking oil to the hydraulic servo 40 of the third clutch C-3 from anoil duct in the boss 3 b. Thereby, in comparison to a structure in whichthe working oil is supplied from an oil duct provided in the input shaft12, it is possible to reduce the number of seal rings, to reduce thesliding resistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₁₀.

In addition, because the hydraulic servo 20 of the first clutch C-1 islocated axially intermediate the planetary gear unit PU and theplanetary gear set DP, it is possible to supply the working oil to thehydraulic servo 20 of the first clutch C-1 from an oil duct in thesupport wall 120. Thereby, in comparison to a structure in which theworking oil is supplied from an oil duct provided in the input shaft 12,it is possible to reduce the number of seal rings, to reduce the slidingresistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₁₀.

Because of provision of a first brake B-1 that selectively locks the sungear S2 to the case 4 against rotation and because the hydraulic servo60 of the first brake B-1 is located on the side of planetary gear unitPU that is axially opposite the planetary gear set DP, the locking forcetransfer member of the first brake B-1 and the sun gear S2 can be linkedwithout making these members complicated, and it is possible to make theautomatic transmission 1 ₁₀ more compact.

In the automatic transmission 1 ₁₀ of the tenth embodiment, the transfermember 103 of the output side of the second clutch C-2 extends aroundthe outer circumference side of the transfer members 101, 102, the hub114 of the fourth clutch C-4, through the transfer member 101, is linkedto the sun gear S2, and the transfer member 104, the transfer member101, the output side of third clutch C-3, and the sun gear S2, whichrotate integrally, are disposed radially inward of the transfer member102. The transfer member 101, which rotates faster than the transfermember 103, is located further toward the radially inner side than thetransfer member 102, which is on the inner circumferential side of thetransfer member 103. Thus, it is possible to make the diameter of thetransfer member 101 of the output side of the fourth clutch C-4, smallerthan the diameter of the transfer member 103 of the output side of thesecond clutch C-2, and to reduce the weight as compared to a structurein which transfer member 101 is on the outer circumferential side. Inaddition, because the inertia is reduced in comparison to a structure inwhich transfer member 101 is disposed on the outer circumferential side,it is possible to improve the controllability of the automatictransmission 1 ₁₀.

The third and first clutches C-3, C-1 are located on the planetary gearset DP side, the transfer members 101, 102 are respectively linked tothe sun gear S2 and the sun gear S3, the fourth clutch C-4 is located onthe side of the planetary gear unit PU that is axially opposite theplanetary gear set DP, the transfer member 101 is linked to the sun gearS2, the second clutch C-2 is located on the planetary gear set DP side,and the transfer member 103 of the output side of the second clutch C-2extends axially with and on the outer circumferential side of thetransfer members 101, 102. Because the transfer member 101, whichrotates faster than the transfer member 103, is on the radially innerside, the diameter of the transfer member 101 can be made smaller thanthe diameter of the transfer member 103, and it is possible to therebyreduce the weight as compared to a structure in which the transfermember 101 is on the outer circumferential side of transfer member 103.In addition, because the inertia is reduced as compared to a structurein which transfer member 101 is on the radially outer side, it ispossible to improve the controllability of the automatic transmission 1₁₀.

Furthermore, because the transfer member of the input side of the fourthclutch C-4 is linked to the carrier CR1 and a portion of the carrier CR1forms a portion of the hydraulic servo 50 of the fourth clutch C-4, itis possible to use portions of the carrier CR1 and the hydraulic servo50 (that is, portions of the clutch drum 52 and the side plate of thecarrier CR1) in common, and thereby reduce size and weight.

Counter gear 15 is linked to the ring gear R3 and is located axiallyintermediate the planetary gear unit PU and the planetary gear set DP. Asupport member 120 a supports the counter gear 15. The hub 112 of thesecond clutch C-2 extends around the outer circumference of the thirdand first clutches C-3, C-1 to link with the carrier CR1. A portion ofthe transfer member 103 of the output side of the second clutch C-2forms as the clutch drum 32 of the hydraulic servo 30 of the secondclutch C-2, and the hydraulic servo 30 is supported on the supportmember 120 a between the planetary gear set DP and the counter gear 15.Therefore, it is possible to supply the working oil to the hydraulicservo 30 of the second clutch C-2 from an oil duct c30 in support member120 a. Thus, in comparison to a structure in which the working oil issupplied from an oil duct in the input shaft 12, it is possible toreduce the number of seal rings, to reduce the sliding friction of theseal rings, and to improve the power transfer efficiency of theautomatic transmission 1 ₁₀.

In addition, boss 3 b holds the sun gear S1 stationary, a portion of thetransfer member of the input side of the third clutch C-3 forms aportion of a clutch drum 42 of the hydraulic servo 40 of the thirdclutch C-3, and the hydraulic servo 40 is supported on the boss 3 baxially intermediate the planetary gear set DP and the side wall 3 a.The transfer member of the input side of the first clutch C-1 is linkedto the transfer member of the input side of the third clutch C-3, and aportion of the transfer member of the input side of the first clutch C-1forms the clutch drum 22 of the hydraulic servo 20 of the first clutchC-1. The hydraulic servo 20 is supported on the support member 120 aaxially intermediate the planetary gear set DP and the hydraulic servo30 of the second clutch C-2. Therefore, it is possible to supply theworking oil to the hydraulic servo 40 of the third clutch C-3 from anoil duct c40. Thus, in comparison to a structure in which, for example,the hydraulic servo 40 of the third clutch C-3 is disposed on the inputshaft 12, spaced from the boss 3 b, and the working oil is supplied viaan oil duct in the input shaft 12, it is possible to shorten the lengthof the oil duct by an amount equivalent to the length of an oil duct inthe input shaft 12, and to improve the controllability of the automatictransmission 1 ₁₀. In addition, it is possible to supply the working oilto the hydraulic servo 20 of the first clutch C-1 from an oil duct c20that extends through the support wall 120 and the support member 120 a.Thus, in comparison to a structure in which, for example, the workingoil is supplied from an oil duct in the input shaft 12, it is possibleto reduce the number of seal rings, to reduce the sliding resistance ofthe seal rings, and to improve the power transfer efficiency of theautomatic transmission 1 ₁₀.

Because a counter shaft 81 is arranged in parallel with the input shaft12 and is linked via the counter gear 15 to the ring gear R3 so as toreceive the output rotation from the ring gear R3, it is possible toadvantageously use the automatic transmission 1 ₁₀ in an FF-typevehicle.

Furthermore, because the counter gear 15 is located axially intermediatethe planetary gear unit PU and the planetary gear set DP and issupported by support member 120 a, it is possible to locate the countergear 15 axially closer to the input side, to position the counter shaftportion 80 and the differential gear portion 90 near the torqueconverter 7 side, and to make the automatic transmission 1 ₁₀ morecompact. It is thereby possible to prevent interference between thedifferential, transmission, etc. and the frame of the vehicle, and tofacilitate the mounting of the automatic transmission 1 ₁₀ in thevehicle.

In addition, because the carrier CR1 is linked to the input shaft 12 onits side facing the planetary gear unit PU and is axially linked to thehub member 112, which is the transfer member of the input side of thesecond clutch C-2, at the side of the planetary gear set DP that isaxially opposite the planetary gear unit PU, it is possible to link thecarrier CR1, the transfer member 112 of the input side of the secondclutch C-2, and the input shaft 12 without making these memberscomplicated, and to make the automatic transmission 1 ₁₀ more compact.

In addition, because the hub 116 of the first brake B-1 and the transfermember 104 are axially linked to the sun gear S2 on the side of theplanetary gear unit PU that is axially opposite the planetary gear setDP, it is possible to link the hub member 116 of the first brake B-1,the transfer member 104, and the sun gear S2 without making thesemembers complicated, and it is possible to make the automatictransmission 1 ₁₀ more compact.

In addition, because the planetary gear set DP includes the sun gear S1,which is held stationary by the case 4, a carrier CR1 that rotatablysupports the pinion gear P1 and the pinion gear P2 and is linked to theoutput shaft 12, and a ring gear R1 that meshes with the pinion gear P2and outputs a reduced speed rotation, it is possible to output a reducedspeed rotation, i.e. at a speed less than that of the input rotation ofthe input shaft 12, from the ring gear R1.

In addition, because the planetary gear unit PU is a Ravigneaux-typeplanetary gear unit PU that includes the sun gear S2, the sun gear S3,the short pinion P3 that meshes with the sun gear S3, the long pinion P4that meshes with the sun gear S2 and with the short pinion P3, thecarrier CR2 that selectively rotatably supports the short pinion P3 andthe long pinion P4, and the ring gear R3 that meshes with the longpinion P4, it is possible to prevent high speed rotation of each of therotary elements and to provide advantageous gear ratios, while enablingthe linking of each of the rotary elements of the planetary gear unit PUand the output side members of each of the clutches and brakes withoutmaking these members complicated.

The first forward speed is established by engaging the first clutch C-1and locking the second brake B-2; the second forward speed isestablished by engaging the first clutch C-1 and locking the first brakeB-1; the third forward speed is established by engaging the first clutchC-1 and the third clutch C-3; the fourth forward speed is established byengaging the first clutch C-1 and the fourth clutch C-4; the fifthforward speed is established by engaging the first clutch C-1 and thesecond clutch C-2; the sixth forward speed is established by engagingthe second clutch C-2 and the fourth clutch C-4; the seventh forwardspeed is established by engaging the second clutch C-2 and the thirdclutch C-3; the eighth forward speed is established by engaging thesecond clutch C-2 and locking the first brake B-1; and reverse speedsare established by engaging the third clutch C-3 or the fourth clutch C4and locking the second brake B-2.

In a velocity diagram in which the respective speeds of the sun gear S2,the sun gear S3, the carrier CR2, and the ring gear R3 of the planetarygear unit PU are shown on the ordinate, and the corresponding gearratios of the sun gear S2, the sun gear S3, and carrier CR2, and thering gear R3 are shown on the abscissa, the sun gear S2 is positioned atthe farthest left end of the ordinate and, in sequence to the rightthereof, are the carrier CR2, the ring gear R3 that is linked to thecounter gear 15, and the sun gear S3.

Eleventh Embodiment

Next, an eleventh embodiment which is a modification of the firstthrough tenth embodiments, will be explained with reference to FIG. 16which is a cross-sectional view of the automatic transmission 1 ₁₁according to the eleventh embodiment.

FIG. 16 shows the schematic structure of the overall automatictransmission 1 ₁₁ of the eleventh embodiment. The relationships of thevarious components will first be explained.

As shown in FIG. 16, the automatic transmission 1 ₁₁ has a speed changemechanism 2 ₁₁ housed in transmission case 3. In the transmission case3, the planetary gear unit PU is disposed around the input shaft 12, andaxially arranged in sequence from the left side, are the second clutchC-2, the first clutch C-1, the planetary gear set DP, the fourth clutchC-4, and the third clutch C-3, on the left side of the planetary gearunit PU. The counter gear 15 and the first brake B-1 are axiallyarranged on the right side of the planetary gear unit PU. The secondbrake B-2 is located on the outer circumferential side of the planetarygear unit PU.

On the left side of the planetary gear unit PU, arranged in axialsequence from the left, are the friction plates 31 of the second clutchC-2, the friction plates 21 of the first clutch C-1, and the frictionplates 41 of the third clutch C-3 are disposed at a relatively outerradial side inside the transmission case 3, while the friction plates 51of the fourth clutch C-4 are located radially inward of the frictionplates 41 of the third clutch C-3.

A boss 3 b extends from the inner side wall portion 3 a of thetransmission case 3, and the hydraulic servo 30 of the second clutch C-2and the hydraulic servo 20 of the first clutch C-1 are supported on theboss 3 b. The planetary gear set DP is located radially inward of thefriction plates 21, and the hydraulic servo 50 of the fourth clutch C-4is disposed adjacent the right side of the planetary gear set DP. Thehydraulic servo 40 of the third clutch C-3 is located to the right sideof the hydraulic servo 50 of the fourth clutch C-4. Specifically, on theleft side of the transmission case 3, supported on the boss 3 b, are thehydraulic servo 30, the hydraulic servo 20, and the planetary gear setDP, and on the intermediate shaft 13, the hydraulic servo 50 and thehydraulic servo 40.

A flange-shaped support wall (center support member) 120 extends fromthe inner circumferential surface of the transmission case 3, andincludes an axially extending leg portion (support member) 120 a whichrotatably supports the counter gear 15 via the ball bearing assembly121.

The friction plates 71 of the second brake B-2 and the hydraulic servo70 of the second brake B-2 are located radially outward of the planetarygear unit PU. The counter gear 15, which is rotatably supported on thesupport member 120 a, is located on the right side of the transmissionin the figure, that is, on the right side of the planetary gear unit PU,and the friction plates 61 of the first brake B-1 and the hydraulicservo 60 of the first brake B-1 are located on the right side of supportwall 120.

In this manner, the hydraulic servo 30 of the second clutch C-2 and thehydraulic servo 20 of the first clutch C-1 are located on the side ofthe planetary gear set DP that is axially opposite the planetary gearunit PU, the hydraulic servo 50 of the fourth clutch C4 and thehydraulic servo 40 of the third clutch C-3 are located axiallyintermediate the planetary gear set DP and the planetary gear unit PU,and the counter gear 15 and the hydraulic servo 60 of the first brakeB-1 are located on the side of the planetary gear unit PU that isaxially opposite the planetary gear set DP.

The structure of the various components inside of the transmission case3 will now be explained with reference to FIG. 16.

The planetary gear set DP includes a sun gear S1, a carrier CR1, and aring gear R1. The sun gear S1 is held stationary by the boss 3 b. Thecarrier CR1 has two carrier plates, right and left, and rotatablysupports the pinions P1 and P2. These pinions P1 and P2 mesh with eachother, and at the same time, the former pinion P1 meshes with the sungear S1 and the latter pinion P2 meshes with the ring gear R1. Theright-side carrier plate is connected to the intermediate shaft 13, andthe left-side carrier plate is connected to the clutch drum 32 that isspline engaged with the outer friction plates 31 of the second clutchC-2. The inner friction plates 21 of the first clutch C-1 are splineengaged with the outer circumferential surface of the ring gear R1. Inaddition, the hub member 113 is connected to the right side of the ringgear R1, and the inner friction plates 41 of the third clutch C-3 arespline engaged with the hub member 113.

The first clutch C-1 is supported on the boss 3 b via the radially innerportion of the clutch drum 32, on the right side of the planetary gearset DP described above. The first clutch C-1 includes friction plates 21and a hydraulic servo 20 that engages/disengages these friction plates21. Hydraulic servo 20 includes a clutch drum 22, a piston member 23, acancel plate 24, and a return spring 25, an oil chamber 26 and thecancel oil chamber 27. The radially inner portion of the clutch drum 22is located on the radially outer side of the radially inner portion ofthe clutch drum 32 of the second clutch C-2, and the outer frictionplates of the friction plates 21 are spline engaged to the innercircumferential surface of the radially outer portion of the clutch drum22. The distal end of the radially outer portion is connected to thetransfer member 102 that links to the sun gear S3 of the planetary gearunit PU. The inner friction plates 21 are spline engaged to the outercircumferential surface of the ring gear R1. The piston member 23 ismounted for axial movement toward and away from the right side of theclutch drum 22, and an oil-tight oil chamber 26 is formed in the spacebetween the piston 23 the clutch drum 22 by the seal rings a1 and a2.The cancel plate 24 is prevented from moving toward the right side by asnap ring 29 that is fit on the clutch drum 22. A return spring 25 iscompressed between the cancel plate 24 and the piston 23 that isdisposed to the left side thereof, and an oil-tight cancel oil chamber27 is formed by the sealing rings a4 and a6.

The second clutch C-2 is disposed on the left side of the first clutchC-1, and is supported on the boss 3 b. The second clutch C-2 includesfriction plates 31 and a hydraulic servo 30 that operates these frictionplates 31. The hydraulic servo 30 includes a clutch drum 32, a piston33, a cancel plate 34, a return spring 35, the oil chamber 36 and thecancel oil chamber 37. The right side portion of the radially innerportion of the clutch drum 32 is linked to the carrier CR1 of theplanetary gear set DP, the hydraulic servo 20 of the first clutch C-1 isdisposed on the radially outer portion on the right side of the clutchdrum 32, and the hydraulic servo 30 is enclosed on its left side by theclutch drum 32. In addition, the outer friction plates 31 are splineengaged to the inner circumferential surface of the radially outerportion of the clutch drum 22, and the inner friction plates 31 arespline engaged to the hub 112. This hub 112 extends around the outercircumference side of the first clutch C-1, the planetary gear set DP,the fourth clutch C-4, and the third clutch C-3, to link with thetransfer member 103 that is connected to the left side plate of thecarrier CR2. The piston 33 is mounted for axial movement on the rightside of the clutch drum 32, and an oil-tight oil chamber 36 is formed inthe space between the piston 33 and the clutch drum 32 by the seal ringsa1 and a2. The cancel plate 34 is prevented from moving toward the rightby a snap ring 39 that is fit on the clutch drum 32. A return spring 35is compressed between the cancel plate 34 and the piston member 33 thatis located to the right of the cancel plate 34, and an oil-tight canceloil chamber 37 is formed by the seal rings a1 and a3.

Because the clutch drum 32 of second clutch C-2 is connected to theinput shaft 12 via the intermediate shaft 13 and the carrier CR1, forreceiving input rotation at the same speed as that of the rotation ofthe input shaft 12, it is possible to provide an input rotational speedsensor on the outer circumferential side of the clutch drum 32 formeasuring the input rotational speed, and, in comparison to anarrangement in which the input rotational speed sensor is located so asto directly measure the rotational of the input shaft 12, it is possibleto more easily mount the input rotational speed sensor.

The fourth clutch C-4, on the right side of the planetary gear unit PU,is located radially inward of the friction plates 41 of the third clutchC-3, and includes friction plates 41 and a hydraulic servo 50 thatengages/disengages the friction plates 51. The inner friction plates 51are spline engaged with the hub 114, and the hub 114 is linked to thetransfer member 101 through the inner circumferential side of thehydraulic servo 40 of the third clutch C-3. The outer friction plates 51are spline engaged with the inner circumferential surface of the clutchdrum 52, the clutch drum 52 shares the right side plate of the carrierCR1 with the input shaft 12, that is, the clutch drum 52 is linked tothe input shaft 12 via the intermediate shaft 13. In this manner, thefourth clutch C-4 can be directly engaged to and released from the inputshaft 12 (intermediate shaft 13) and the sun gear S2, and not, forexample, through the carrier CR1 of the planetary gear set DP.

The hydraulic servo 50 includes the clutch drum 52, a piston 53, acancel plate 54, a return spring 55, an oil chamber 56 and the canceloil chamber 57. As described above, the inner circumferential side ofthe clutch drum 52 is connected to the intermediate shaft 13, and aportion of the outer circumferential surface of the intermediate shaft13 and hydraulic servo 50 is formed by portions of the outercircumferential surface of the intermediate shaft 13 and the clutch drum52. The piston 53 is mounted for axial movement toward and away from theclutch drum 52, and an oil-tight oil chamber 56 is formed between thepiston 53 and the clutch drum 52 by the seal rings a7 and a8. Thus, aportion of the clutch drum serves as the cylinder of hydraulic servo 50.The piston 53 is arranged to engage the front surface of the frictionplates 51. Furthermore, the cancel plate 54 is prevented from movingtoward the right side by a snap ring 59 that is fit on the outercircumferential surface of the radially inner portion of the clutch drum52 described above, and a return spring 55 is compressed between thecancel plate 54 and the piston 53 that is disposed on the left sidethereof to form an oil-tight cancel oil chamber 57 via the seal rings a7and a9.

The third clutch C-3 is on the right side of the fourth clutch C-4 issupported on the intermediate shaft 13 via the transfer member 101, andincludes friction plates 41 and a hydraulic servo 40 thatengages/disengages these friction plates 41. The inner friction plates41 are spline engaged to the outer circumferential surface of the hub113, which is linked to the ring gear R1 as described above. The outerfriction plates 41 are spline engaged to the inner circumferentialsurface of the clutch drum 42, and the clutch drum 42 is linked to thetransfer member 101, which in turn is linked to the sun gear S2 of theplanetary gear unit PU.

The hydraulic servo 40 includes a clutch drum 42, a piston 43, a cancelplate 44, and a return spring 45, the oil chamber 46 and the cancel oilchamber 47. At its inner circumference, the clutch drum 42 is connectedto the transfer member 101, and a hydraulic servo 40 is formed byportions of the outer circumferential surface of the transfer member 101and the clutch drum 42. The piston 43 is mounted for axial movementrelative to the clutch drum 42, and an oil-tight oil chamber 46 isformed between the piston 43 and the clutch drum 42 by the seal ringsa10 and a11. An outer radial extension of the piston 43 is axiallyopposite the front surface of the friction plates 41. The cancel plate44 is prevented from moving toward the left by a snap ring 49 that isfit on the outer circumferential surface of the transfer member 101, anda return spring 45 is compressed between the cancel plate 44 and thepiston 43 that is disposed on the right side thereof, and an oil-tightcancel oil chamber 47 is formed by the seal rings a10 and a12.

The second brake B-2 is located radially outward of the ring gear R3 ofthe planetary gear unit PU. The second brake B-2 includes frictionplates 71 and a hydraulic servo 70 that operates these friction plates71. The outer friction plates 71 are spline engaged to the innercircumferential surface of the transmission case 3, and the innerfriction plates 71 are spline engaged to the hub 117 that is linked tothe transfer member 103 described above (specifically, linked to thecarrier CR2 of the planetary gear unit PU).

The hydraulic servo 70 includes a cylinder 72, a piston 73, a cancelplate 74, a return spring 75, and oil chamber 76 which is formed betweenthe cylinder 72 and the piston 73. The piston 73 is mounted for axialmovement, and its left side end is axially opposite the friction plates71. An oil-tight oil chamber 76 is formed between the piston 73 and thetransmission case 3 by the two seal rings a15 and a16. The cancel plate74 is prevented from moving toward the left side by a snap spring 79that is fit on the inner circumferential surface of the transmissioncase 3.

The first brake B-1 extends between the right side inner surface of thetransmission case 3 and the partition wall 3 c that separates thetransmission case 3 and a housing case (not illustrated). The firstbrake B-1 includes friction plates 61 and a hydraulic servo 60 thatoperates these friction plates 61. The outer friction plates 61 arespline engaged to the inner circumferential surface of the transmissioncase 3, and the inner friction plates 61 are spline engaged to the hub116 that is connected to the sun gear S2 of the planetary gear unit PUvia the transfer member 104.

The hydraulic servo 60 includes a piston 63, a cancel plate 64, a returnspring 65, and an oil chamber 66 formed in the space between the piston63 and the cylinder formed by the partition wall 3 c. The piston 63 ismounted for axial movement with its left side end axially aligned withthe friction plates 61 in opposition thereto. An oil-tight oil chamber66 is formed between the piston 63 and the cylindrical recess in thepartition wall portion 3 c by the two seal rings a13 and a14. The cancelplate 64 is prevented from moving toward the left by a snap spring 69that is fit within the cylindrical recess in the partition wall 3 c.

The planetary gear unit PU includes a sun gear S2, a sun gear S3, ashort pinion P3 that meshes with the sun gear S3, a long pinion P4 thatmeshes with the sun gear S2 and the short pinion P3, and a carrier CR2that rotatably supports the short pinion P3 and the long pinion P4between side plates, and a ring gear R3 that meshes with the long pinionP4 to form what is termed a Ravigneaux planetary gear set.

A transfer member 104 that passes through the inner circumferential sideof the counter gear 15 is linked to the right side of the sun gear S2,and the sun gear S2 connects to the hub 116 of the first brake B-1 viathis transfer member 104. In addition, the transfer member 101 describedabove is linked to the left side of the sun gear S2, and the sun gear S2is linked to the hub 114 of the fourth clutch C-4 and the clutch member101 of the third clutch C-3 via this transfer member 101. The transfermember 102 is linked to the left side of the sun gear S3, and the sungear S3 is linked to the clutch drum 22 of the first clutch C-1 via thislinking member 102.

The left side plate of the carrier CR2, that is, the plate on theplanetary gear set DP side, is linked to the transfer member 103, andthe carrier CR2 is linked to the hub member 112 of the second clutch C-2via this transfer member 103. In addition, the carrier CR2 is linked tothe hub 117 of the second brake B-2 via this transfer member 103. Thering gear R3 is linked to the counter gear 15 via the transfer member105. The counter gear 15 meshes with the large diameter gear 82 that islinked with the counter shaft 81 to transfer rotation to the left andright wheels 93 l and 93 r (that is, the drive wheels) via the countershaft portion 80 and the differential gear portion 90.

Next, the structure of each of the oil ducts and the supply of theworking oil will be briefly explained. The oil duct c30 in the boss 3 bcommunicates with the oil chamber 36 of the hydraulic servo 30 of thesecond clutch C-2, that is, the oil chamber 36 that is formed by sealingthe space between the clutch drum 32 and the piston 33 by the seal ringsa1 and a2. Oil is supplied through the space between the clutch drum 32and the boss 3 b defined between the seal rings d1 and d2, from an oilduct (not illustrated) to the cancel oil chamber 37 that is formed bysealing the space between the piston 33 and the cancel plate 34 with theseal rings a1 and a3.

In addition, the oil duct c20 in the boss 3 b communicates with the oilchamber 26 of the hydraulic servo 20 of the first clutch C-1, that is,the oil chamber 26 that is formed by sealing the space between theclutch drum 22 and the piston member 23 with the seal rings a4 and a5.This supply is through the space between the clutch drum 32 of thesecond clutch C-2 and the boss 3 b defined between the seal rings d3 andd4 and through the space between the clutch drum 32 and the clutch drum22 defined between the seal rings d5 and d6. Note that oil is suppliedfrom an oil duct (not illustrated) to the cancel oil chamber 27 that isformed by sealing the space between the piston member 23 and the cancelplate 24 by the seal rings a4 and a6.

In addition, the oil duct c50 in the boss 3 b communicates, via the oilduct c51 in the intermediate shaft 13, an axial oil duct (notillustrated), and the oil duct c53, with the oil chamber 56 of thehydraulic servo 50 of the fourth clutch C-4, that is, the oil chamber 56formed by sealing the space between the clutch drum 52 and the pistonmember 53 by the sealing rings a7 and a8. This communication is throughthe space between the boss 3 b and the intermediate shaft 13 definedbetween the seal rings d9 and d10. Note that oil is supplied from an oilduct (not illustrated) to the cancel oil chamber 57 that is formed bysealing the space between the piston member 53 and the cancel plate 54with the seal rings a7 and a9.

In addition, the oil duct c40 in the boss 3 b communicates, via the oilducts c41, c42, and c43 in the intermediate shaft 13, with the oilchamber 46 of the hydraulic servo 40 of the third clutch C-3, that is,the oil chamber 46 formed by sealing the space between the clutch drum42 and the piston member 43 with the seal rings a10 and a11. Thiscommunication is through a the space between the boss 3 b and theintermediate shaft 13 defined by the seal rings d7 and d8 and by sealingthe space between the intermediate shaft 13 and the transfer member 101(that is, the clutch drum) defined between the seal rings d11 and d12.Note that oil is also supplied from an oil duct (not illustrated) to thecancel oil chamber 47 that is formed by sealing the space between thepiston member 43 and the cancel plate 44 by the seal rings a10 and a12.

In addition, working oil is supplied from an oil duct (not illustrated)in the partition wall portion 3 c to the oil chamber 66 of the hydraulicservo 60 of the first brake B-1, that is, the oil chamber 66 that isformed by sealing the space between the side wall 3 c of thetransmission case 3 and the piston member 63 with the seal rings a13 anda14.

In addition, working oil is supplied from an oil duct in thetransmission case 3 (not illustrated) to the oil chamber 76 of thehydraulic servo 70 of the second brake B-2, that is, the oil chamber 76that is formed by sealing the space between the cylinder member 72 andthe piston member 73 by the seal rings a15 and a16.

An oil duct c80 extends axially within the input shaft 12 and theintermediate shaft 13, and receives lubricating oil from an oil duct(not illustrated) in the boss 3 b. A plurality of holes (notillustrated) bored into the input shaft 12 and the intermediate shaft 13extend radially from the oil duct c80, through which lubricating oil issupplied to the speed change mechanism 2 ₁₁ in the form of a spray.

An axial oil duct c90 formed in the input shaft 12 communicates with thelock-up clutch 10 described above via an oil duct (not illustrated), andresponsive to supply of working oil from a hydraulic control apparatus(not illustrated) via an oil duct (not illustrated) in the partitionwall 3 c, the lock-up clutch 10 is engaged.

The automatic transmission 1 ₁₁ eliminates a member enclosing theplanetary gear unit PU because the fourth clutch C-4 is interposed inthe transfer path to connect input shaft 12 and the sun gear S2, thesecond clutch C-2 is interposed in the transfer path to connect thecarrier CR1 and the carrier CR2, and the output side transfer member 103of the second clutch C-2 is axially linked to the side of the carrierCR2 facing the planetary gear set DP. The automatic transmission 1 ₁₁ isthereby made more radially compact. In addition, it is possible toshorten the transfer member, which requires a high rigidity, to reducethe weight, and to improve the controllability of the automatictransmission. Furthermore, the structure enables lubricating oil to bereadily discharged where needed, and to ensure the coolingcapacity/performance. In addition, it is possible to simplify theassembly of the automatic transmission 1 ₁₁ for a vehicle. Furthermore,the configuration of each of the clutches enables supply of working oilthereto from the support wall 120. Thus, it is possible to reduce thenumber of seal rings, to reduce the sliding resistance of the sealrings, and to improve the power transfer efficiency of the automatictransmission 1 ₁₁.

In addition, because the hydraulic servo 50 of the fourth clutch C-4 islocated axially intermediate the planetary gear unit PU and theplanetary gear set DP and adjacent the planetary gear set DP, it ispossible to partially form the carrier CR1 and the clutch drum 52 (thatis, the clutch drum 52 and the side plate of the carrier CR1) in common,and it is possible to reduce the size and weight.

Furthermore, because the hydraulic servo 30 second clutch C-2 is locatedon the side of the planetary gear set DP that is axially opposite theplanetary gear unit PU, it is possible to supply the working oil fromthe oil duct that is provided in the boss 3 b to the hydraulic servo 30of the second clutch C-2. Thereby, in comparison to a structure in whichthe working oil is supplied from an oil duct in the input shaft 12, itis possible to reduce the number of seal rings, to reduce the slidingresistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₁₁.

Furthermore, because the hydraulic servo 40 of the third clutch C-3 islocated axially intermediate the planetary gear unit PU and theplanetary gear set DP, in comparison to a structure in which thehydraulic servo 40 of the third clutch C-3 is located on the side of theplanetary gear set DP that is axially opposite the planetary gear unitPU, it is possible to shorten the distance between the third clutch C-3and the planetary gear unit PU, and to shorten the output side transfermember of the third clutch C-3, which requires strength for transferringa high torque. Thereby, it is possible to reduce the weight, and toimprove the controllability of the automatic transmission 1 ₁₁.

Furthermore, because the hydraulic servo 20 of the first clutch C-1 isdisposed on the side of the planetary gear set DP that is axiallyopposite the planetary gear unit PU, it is possible to supply theworking oil to the hydraulic servo 20 of the first clutch C-1 from anoil duct in the boss 3 b. Thereby, in comparison to a structure in whichworking oil is supplied from an oil duct in the input shaft 12, it ispossible to reduce the number of seal rings, to reduce the slidingresistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₁₁.

Because first brake B-1 that selectively locks the rotation of the sungear S2 has a hydraulic servo 60 located on the side of counter gear set15 that is axially opposite the planetary gear unit PU, and because thelocking force transfer member of the first brake B-1 links to the sungear S2 by passing through the inner circumferential side of the countergear 15, it is possible to link the locking force transfer member of thefirst brake B-1 and the sun gear S2 without making these memberscomplicated, and to make the automatic transmission 1 ₁₁ more compact.

In the automatic transmission 1 ₁₁ according to the present invention asexplained above, the transfer member 103 of the output side of thesecond clutch C-2 extends coaxially with and radially outward of thetransfer members 101, 102 of the output side of the third and firstclutches C-3, C-1. The transfer member 101 of the output sides of thefourth clutch C-4 and the third clutch C-3 is linked to the sun gear S2,and the transfer member 104 of the output sides of the fourth clutch C-4and the third clutch C-3, which rotate integrally, are disposed radiallyinward of the transfer member 102 of the output side of the first clutchC-1. Thereby, the transfer member 101 of the output side of the fourthclutch C-4, which rotates faster than the transfer member 103 of theoutput side of the second clutch C-2, is further radially inward thanthe transfer member 102 of the output side of the first clutch C-1,which, in turn, is radially inward of the transfer member 103 of theoutput side of the second clutch C-2. Therefore, the diameter of thetransfer member 101 of the output side of the fourth clutch C4 issmaller than the diameter of the transfer member 103 of the output sideof the second clutch C-2, and it is possible to reduce the weight ascompared to a structure in which transfer member 101 is the radiallyoutermost member. In addition, because the inertia is reduced incomparison to a structure in which the transfer member 101 is disposedon the radially outer side, it is possible to improve thecontrollability of the automatic transmission 1 ₁₁.

In addition, the third and first clutches C-3, C-1 are disposed on theplanetary gear set DP, the transfer members 101, 102 of the output sidesof the third and first clutches C-3, C-1 are linked respectively to thesun gear S2 and the sun gear S3, the fourth clutch C-4 is disposed onthe side of the planetary gear unit PU that is axially opposite theplanetary gear set DP, the transfer member 101 of the output side of thefourth clutch C-4 is linked to the sun gear S2, the second clutch C-2 islocated on the planetary gear set DP side, and the transfer member 103of the output sides of the second clutch C-2, C-1 extends around theouter circumference of the transfer members 101, 102 to link to thecarrier CR2. Thereby, because the transfer member 101 of the output sideof the fourth clutch C-4, which rotates faster than the transfer memberof the output side of the second clutch C-2, is on the radially innerside, the diameter of the transfer member 101 can be made smaller thanthe diameter of the transfer member 103, and it is possible to reducethe weight as compared to a structure in which transfer member 101 isdisposed on the outer side. In addition, because it is possible toreduce the inertia in comparison to a structure in which transfer member101 is on the outside, it is possible to improve the controllability ofthe automatic transmission 1 ₁₁.

Furthermore, because the transfer member of the input side of the fourthclutch C4 is directly linked to the carrier CR1 and a portion of thecarrier CR1 forms a portion of the hydraulic servo 50, i.e. becauseportions of the clutch drum 52 and the side plate of the carrier CR1 areused in common, it is possible to reduce the weight and size.

Because the transfer member of the input side of the second clutch C-2is linked to the carrier CR1, because a portion of the transfer memberof the input side of the second clutch C-2 forms a portion of the clutchdrum 32, and because the hydraulic servo 30 is supported on the boss 3 baxially intermediate the planetary gear set DP and the side wall 3 a, itis possible to supply the working oil to the hydraulic servo 30 of thesecond clutch C-2 from an oil duct c30 in the boss 3 b. Thus, incomparison to a structure in which, for example, the hydraulic servo 30of the second clutch C-2 is disposed on the input shaft 12, separatedfrom the boss 3 b, and the working oil is supplied via an oil duct inthe input shaft 12, it is possible to shorten the length of the oil ductby the length of an oil duct in the input shaft 12, and it is possibleto improve the controllability of the automatic transmission 1 ₁₁.

In addition, because the hub 111 of the first clutch C-1 is linked tothe ring gear R1, because the transfer member 102 clutch C-1 is linkedto the sun gear S3, because a portion of the transfer member 102 ofclutch C-1 forms as the clutch drum 22 of the hydraulic servo 20 of thefirst clutch C-1, and because the hydraulic servo 20 is mounted on theboss 3 b axially intermediate the planetary gear set DP and thehydraulic servo 20 of the first clutch C-1, it is possible to supply theworking oil to the hydraulic servo 20 of the first clutch C-1 from anoil duct c20 in the boss 3 b. Thus, in comparison to a structure inwhich, for example, the hydraulic servo 20 of the first clutch C-1 isdisposed on the input shaft 12, separated from the boss 3 b, and theworking oil is supplied via an oil duct in the input shaft 12, it ispossible to shorten the length of an oil duct in the input shaft 12, andto improve the controllability of the automatic transmission 1 ₁₁.

In addition, because a counter gear 15, which is linked to the ring gearR3 of the planetary gear unit PU, is located on the side of theplanetary gear unit PU that is axially opposite the planetary gear setDP, and because the friction plates 71 of brake B-2 are located radiallyoutward of the planetary gear unit PU, the hub member 117 of the secondbrake B-2 can use the transfer member 103 and the output side of thesecond clutch C-2 in common to link to the carrier CR2 and, as compared,for example, to a structure in which a band brake is disposed around theouter circumference of the transfer member 103, it is possible todispose multi-plate brakes in a space on the radially outer side of theplanetary gear unit PU, in a relatively compact structure.

Furthermore, because a counter shaft 81 is arranged in parallel with theinput shaft 12 and linked to the counter gear 15 to receive the outputrotation from the ring gear R3, the automatic transmission 1 ₁₁ isadvantageously used in an FF-type vehicle.

In addition, because the counter gear 15 is located on the side of theplanetary gear unit PU that is axially opposite the planetary gear setDP and is supported by the support member 120 a, it is possible toshorten the distance between the planetary gear set DP and the planetarygear unit PU, and to shorten the output side member 101 of the thirdclutch C-3 and the output side member 102 of the first clutch C-1, whichmust in particular be strong in order to transfer a high torque.Thereby, it is possible to reduce the weight and to improve thecontrollability of the automatic transmission 1 ₁₁.

Because the carrier CR1 is connected to the input shaft 12 on its sidefacing the planetary gear unit PU and is linked to the clutch drum 32,which is the transfer member of the input side of the second clutch C-2,on its side axially opposite the planetary gear unit PU, it is possibleto link the carrier CR1, the transfer member 112 of the input side ofthe second clutch C-2, and the input shaft 12 without making thesemembers complicated, and it is possible to make the automatictransmission 1 ₁₁ more compact.

In addition, because the hub 116 of the first brake B-1 and the transfermember 104 that is linked thereto are axially linked to the sun gear S2at a side of the planetary gear unit PU that is axially opposite theplanetary gear set DP, it is possible to link the hub member 116 of thefirst brake B-1, the transfer member 104, and the sun gear S2 withoutmaking these members complicated, and to make the automatic transmission1 ₁₁ more compact.

With the planetary gear set DP which includes a sun gear S1 which isheld stationary on the case 4, a carrier CR1 that rotatably supports thepinion gear P1 and the pinion gear P2 and is linked to the input shaft12, and a ring gear R1 that meshes with the pinion gear P2 and outputs areduced speed rotation, it is possible to output a reduced speedrotation less than that of the input rotation of the input shaft 12 atthe ring gear R1.

In addition, because the planetary gear unit PU is a Ravigneaux-typeplanetary gear unit PU that includes a sun gear S2, a sun gear S3, shortpinion P3 that meshes with the sun gear S3, a long pinion P4 that mesheswith the sun gear S2 and with the short pinion P3, a carrier CR2 thatrotatably supports the short pinion P3 and the long pinion P4, and thering gear R3 that meshes with the long pinion P4, it is possible toprevent high speed rotation of each of the rotary members, and it ispossible to provide favorable gear ratios while enabling each of therotary elements of the planetary gear unit PU and the output sidemembers of each of the clutches and brakes to be linked without makingthese members complicated.

The first forward speed is established by engaging the first clutch C-1and locking the second brake B-2; the second forward speed isestablished by engaging the first clutch C-1 and locking the first brakeB-1; the third forward speed is established by engaging the first clutchC-1 and the third clutch C-3; the fourth forward speed is established byengaging the first clutch C-1 and the fourth clutch C-4; the fifthforward speed is established by engaging the first clutch C-1 and thesecond clutch C-2; the sixth forward speed is established by engagingthe second clutch C-2 and the fourth clutch C-4; the seventh forwardspeed is established by engaging the second clutch C-2 and the thirdclutch C-3; the eighth forward speed is established by engaging thesecond clutch C-2 and locking the first brake B-1; and reverse speedsare established by engaging the third clutch C-3 or the fourth clutchC-4 and locking the second brake B-2.

In a velocity diagram in which the respective speeds of the sun gear S2,the sun gear S3, the carrier CR2, and the ring gear R3 of the planetarygear unit PU are shown on the ordinate, and the corresponding gearratios of the sun gear S2, the sun gear S3, the carrier CR2, and thering gear R3 are shown on the abscissa, the sun gear S2 is positioned atthe farthest left end of the ordinate and, in sequence to its right, arethe carrier CR2, the ring gear R3 that is linked to the counter gear 15,and the sun gear S3.

The automatic transmission 1 ₁₁ according to the eleventh embodimentsubstantially becomes an automatic transmission 1 ₁₃ according to thethirteenth embodiment described below by rotating the speed changemechanism 2 ₁₁ left-right.

Twelfth Embodiment

Next, a twelfth embodiment, in which a portion of the eleventhembodiment has been modified, will be explained with reference to FIG.17 which is a cross-sectional view of the automatic transmission 1 ₁₂according to the twelfth embodiment. In describing the twelfthembodiment below, only those features that differ from the automatictransmission 1 ₁₁ of the eleventh embodiment will be explained, theothers are substantially identical and the explanation thereof will beomitted.

In the automatic transmission 1 ₁₂ according to the twelfth embodiment,in contrast to the automatic transmission 1 ₁₁ according to the eleventhembodiment, the hydraulic servo 50 of the fourth clutch C-4 is locatedon the side of the planetary gear unit PU that is axially opposite theplanetary gear unit PU. Specifically, the hydraulic servo 50 of thefourth clutch C-4 is disposed adjacent the support wall 120, to theright of the counter gear 15, on the boss 3 d that extends from thepartition wall 3 c.

The hydraulic servo 30 of the second clutch C-2 and the hydraulic servo20 of the first clutch C-1 are located on the side of the planetary gearset DP that is axially opposite the planetary gear unit PU, thehydraulic servo 40 of the third clutch C-3 is located axiallyintermediate the planetary gear set DP and the planetary gear unit PU,and the counter gear 15, the hydraulic servo 50 of the fourth clutchC-4, and the hydraulic servo 60 of the first brake B-1 are located onthe side of the planetary gear unit PU that is axially opposite theplanetary gear set DP.

Because the fourth clutch C-4 is interposed in the transfer path toconnect the input shaft 12 and the sun gear S2, the second clutch C-2 isinterposed in the transfer path to connect the carrier CR1 and thecarrier CR2, and the output side transfer member 103 of the secondclutch C-2 is linked to the side of the carrier CR2 axially facing theplanetary gear set DP, it is possible to eliminate a member thatencloses the planetary gear unit PU. Thereby, the automatic transmission1 ₁₂ can be made more radially compact. In addition, it is possible toshorten the transfer member that requires a high rigidity, it ispossible to reduce the weight, and it is possible to improve thecontrollability of the automatic transmission 1 ₇. Furthermore, thestructure allows lubricating oil to be readily discharged where needed,and the cooling performance to be ensured. In addition, the assembly ofthe automatic transmission 1 ₁₂ is simplified. Furthermore, because theworking oil for the clutches can be supplied from support wall 120 dueto the configuration of each of the clutches, it is possible to reducethe number of seal rings, to reduce the sliding resistance of the sealrings, and to improve the power transfer efficiency of the automatictransmission 1 ₁₂.

In addition, because the hydraulic servo 30 of the second clutch C-2 islocated on the side of the planetary gear set DP that is axiallyopposite the planetary gear unit PU, it is possible to supply theworking oil to the hydraulic servo 30 of the second clutch C-2 from anoil duct provided in the boss 3 b that extends from one end of the case4. Thereby, in comparison to a structure in which the working oil issupplied from an oil duct in the input shaft 12, it is possible toreduce the number of seal rings, to reduce the sliding resistance of theseal rings, and to improve the power transfer efficiency of theautomatic transmission 1 ₁₂.

Furthermore, because the hydraulic servo 50 of the fourth clutch C-4 isdisposed on the side of the planetary gear unit PU that is axiallyopposite the planetary gear set DP and the friction plates 51 arelocated more radially outward, it is possible to enlarge the surfacearea of the friction plates 51 and to ensure transfer of a sufficienttorque, while reducing the number of friction plates 51. Furthermore, itis possible to supply working oil to the hydraulic servo 50 of thefourth clutch C-4 from an oil duct provided in the boss 3 d that extendsfrom one end of the case 4. Thereby, in comparison to a structure inwhich the working oil is supplied from an oil duct in the input shaft12, it is possible to reduce the number of seal rings, to reduce thesliding resistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₁₂.

In addition, because the hydraulic servo 40 of the third clutch C-3 islocated axially intermediate the planetary gear unit PU and theplanetary gear set DP, in comparison to a structure in which thehydraulic servo 40 of the third clutch C-3 is located on the side of theplanetary gear set DP that is axially opposite the planetary gear unitPU, it is possible to shorten the distance between the third clutch C-3and the planetary gear unit PU, and to shorten the output side transfermember 101 of the third clutch C-3, which requires strength fortransferring a high torque. Thereby, it is possible to reduce the weightand to improve the controllability of automatic transmission 1 ₁₂.

Likewise, because the hydraulic servo 20 of the first clutch C-1 islocated on the side of the planetary gear set DP that is axiallyopposite the planetary gear unit PU, it is possible to supply theworking oil to the hydraulic servo 20 of the first clutch C-1 from anoil duct in the boss 3 b. Thereby, in comparison to a structure in whichthe working oil is supplied from an oil duct in the input shaft 12, itis possible to reduce the number of seal rings, to reduce the slidingresistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₁₂.

The first brake B-1 that selectively locks the rotation of the sun gearS2 has a hydraulic servo 60 located on the side of the counter gear 15that is axially opposite the planetary gear set DP, and a locking forcetransfer member linked to the sun gear S2 and extending along theradially inner side. Therefore, it is possible to link the locking forcetransfer member of the first brake B-1 and the sun gear S2 withoutmaking these members complicated, and to make the automatic transmission13 more compact.

The transfer member 103 of the output side of the second clutch C-2 islinked to the carrier CR2 and extends coaxial with and radially outwardof the transfer members 101, 102 of the output sides of the third andfirst clutches C-3, C-1. The transfer member 104 of the output side ofthe fourth clutch C-4 and the transfer member 101 of the output side ofthe third clutch C-3 are linked to the sun gear S2, and the transfermember 104, the transfer member 101, and the sun gear S2, which rotateintegrally, are disposed radially inward of the transfer member 102.Therefore, the transfer member 104, which rotates faster than thetransfer member 103, is further radially inward than the transfer member102, which is inward of the transfer member 103. Thus, the diameter ofthe transfer member 104 is smaller than the diameter of the transfermember 103, and it is possible to reduce the weight as compared to astructure in which the transfer member is on the radially outer side. Inaddition, because the inertia is reduced in comparison to a structure inwhich it is disposed on the radially outer side, it is possible toimprove the controllability of the automatic transmission 1 ₁₂.

Because the transfer member of the input side of the second clutch C-2forms a portion of a clutch drum 32 of the hydraulic servo 30 of thesecond clutch C-2, and because the hydraulic servo 30 is supported onthe boss 3 b axially intermediate the planetary gear set DP and the sidewall 3 a, it is possible to supply the working oil to the hydraulicservo 30 of the second clutch C-2 from an oil duct c30 in the boss 3 b.Thus, in comparison to a structure in which, for example, the hydraulicservo 30 of the second clutch C-2 is disposed on the input shaft 12,separated from the boss 3 b, and the working oil is supplied via an oilduct in the input shaft 12, it is possible to shorten the length of theoil duct by an amount equivalent to the length of an oil duct in theinput shaft 12, and to improve the controllability of the automatictransmission 1 ₁₂.

In addition, because the hub 111 of the first clutch C-1 is linked tothe ring gear R1, the transfer member 102 of the output side of thefirst clutch C-1 is linked to the sun gear S3, a portion of the transfermember 102 forms the clutch drum 22 of the hydraulic servo 20 of thefirst clutch C-1, and the hydraulic servo 20 is supported on the boss 3b axially intermediate the planetary gear set DP and the hydraulic servo20 of the first clutch C-1, it is possible to supply the working oil tothe hydraulic servo 20 of the first clutch C-1 from an oil duct c20 inthe boss 3 b. Thus, in comparison to a structure in which, for example,the hydraulic servo 20 of the first clutch C-1 is disposed on the inputshaft 12, separated from the boss 3 b, and the working oil is suppliedvia an oil duct in the input shaft 12, it is possible to shorten thelength of the oil duct by an amount equivalent to the length of the oilduct in the input shaft 12, and it is possible to improve thecontrollability of the automatic transmission 1 ₁₂.

In addition, because counter gear 15 is located on the side of theplanetary gear unit PU that is axially opposite the planetary gear setDP, and because the multi-plate brakes are disposed around the outercircumference of the planetary gear unit PU, in comparison to astructure in which, for example, the counter gear 15 is between theplanetary gear unit PU and the planetary gear set DP, the hub member 117of the second brake B-2 can use the transfer member 103 of the outputside of the second clutch C-2 in common to link to the carrier CR2.Also, in comparison to a structure in which a band brake is disposedaround the outer circumference of the transfer member 103 of the outputside of the second clutch C-2, it is possible to use multi-plate brakes,located radially outward of the planetary gear unit PU, whilemaintaining compactness.

Furthermore, because a counter shaft 81 is arranged in parallel with theinput shaft 12 and is linked to the counter gear 15 to receive theoutput rotation from the ring gear R3, it is possible to advantageouslyuse the automatic transmission 1 ₁₂ in an FF-type vehicle.

In addition, because the counter gear 15 is located on the side of theplanetary gear unit PU that is axially opposite the planetary gear setDP and is supported by the support member 120 a, it is possible toshorten the distance between the planetary gear set DP and the planetarygear unit PU, and to shorten the output side member 101 of the thirdclutch C-3 and the output side member 102 of the first clutch C-1, whichmust in particular be strong in order to transfer a high torque.Thereby, it is possible to reduce the weight and to improve thecontrollability of the automatic transmission 1 ₁₂.

In addition, because the carrier CR1 is linked to the input shaft 12 onthe side facing planetary gear unit PU and is linked to the hub member112 at the side of the planetary gear set DP that is axially oppositethe planetary gear unit PU, it is possible to link the carrier CR1, thetransfer member 112 of the input side of the second clutch C-2, and theinput shaft 12 without making these members complicated, to make theautomatic transmission 1 ₁₂ more compact.

In addition, because the hub 116 of the first brake B-1 and the transfermember 104 that is linked thereto are axially linked to the sun gear S2on the side of the planetary gear unit PU that is axially opposite theplanetary gear set DP, it is possible to link the hub 116 of the firstbrake B-1, the transfer member 104, and the sun gear S2 without makingthese members complicated, and to make the automatic transmission 1 ₁₂more compact.

The planetary gear set DP includes a non-rotatable sun gear S1, acarrier CR1 that rotatably supports the pinion gear P1 and the piniongear P2 and is linked to the input shaft 12, and a ring gear R1 thatmeshes with the pinion gear P2 and outputs a reduced speed rotation, andprovides output of a reduced speed rotation, i.e. at a speed less thanthat of the input rotation of the input shaft 12, at the ring gear R1.

Because the planetary gear unit PU is a Ravigneaux-type planetary gearunit PU that includes a sun gear S2, a sun gear S3, short pinion P3 thatmeshes with the sun gear S3, a long pinion P4 that meshes with the sungear S2 and with the short pinion P3, a carrier CR2 that rotatablysupports the short pinion P3 and the long pinion P4, and the ring gearR3 that meshes with the long pinion P4, it is possible to prevent highspeed rotation of the rotary members and to provide favorable gearratios while enabling each of the rotary elements of the planetary gearunit PU and the output side members of each of the clutches and brakesto be linked without making these members complicated.

The first forward speed is established by engaging the first clutch C-1and locking the second brake B-2; the second forward speed isestablished by engaging the first clutch C-1 and locking the first brakeB-1; the third forward speed is established by engaging the first clutchC-1 and the third clutch C-3; the fourth forward speed is established byengaging the first clutch C-1 and the fourth clutch C-4; the fifthforward speed is established by engaging the first clutch C-1 and thesecond clutch C-2; the sixth forward speed is established by engagingthe second clutch C-2 and the fourth clutch C-4; the seventh forwardspeed is established by engaging the second clutch C-2 and the thirdclutch C-3; the eighth forward speed is established by engaging thesecond clutch C-2 and locking the first brake B-1; and reverse speedsare established by engaging the third clutch C-3 or the fourth clutchC-4 and locking the second brake B-2.

In a velocity diagram in which the respective speeds of the sun gear S2,the sun gear S3, the carrier CR2, and the ring gear R3 of the planetarygear unit PU are shown on the ordinate, and the corresponding gearratios of the sun gear S2, the sun gear S3, the carrier CR2, and thering gear R3 are shown in the abscissa, the sun gear S2 is positioned atthe farthest left end of the ordinate and, arranged in sequence to itsright, are the carrier CR2, the ring gear R3, and the sun gear S3.

Thirteenth Embodiment

The thirteenth embodiment may be regarded as a modification of theeleventh embodiment. FIG. 18 is a cross-sectional view of the automatictransmission 1 ₁₃ of the thirteenth embodiment. In the description ofthe thirteenth embodiment which follows, features having a structurethat is identical to the automatic transmission 1 ₁₁ of the eleventhembodiment are denoted by identical reference numerals, and theexplanation thereof is omitted.

In the automatic transmission 1 ₁₃ of the thirteenth embodiment, theinput shaft 12 and the intermediate shaft 13 and engine orientation arenot changed. However, the orientations of the first through fourthclutches C-1 to C-4, the first and second brakes B-1 and B-2, theplanetary gear set DP, the planetary gear unit PU, and the counter gear15 are substantially reversed right-left, i.e. the speed changemechanism 2 ₁₃ is substantially the speed change mechanism 2 ₁₁ rotated180° right-left.

The hydraulic servo 30 of the second clutch C-2 and the hydraulic servo20 of the first clutch C-1 are located on the side of the planetary gearset DP that is axially opposite the planetary gear unit PU. Thehydraulic servo 50 of the fourth clutch C-4 and the hydraulic servo 40of the third clutch C-3 are located axially intermediate the planetarygear set DP and the planetary gear unit PU, and the counter gear 15 andthe hydraulic servo 60 of the first brake B-1 are located on the side ofthe planetary gear unit PU that is axially opposite the planetary gearset DP.

In automatic transmission 1 ₁₃ described above, because the fourthclutch C-4 is interposed in the transfer path to connect the input shaft12 and the sun gear S2, the second clutch C-2 is interposed in thetransfer path to connect the carrier CR1 and the carrier CR2, and theoutput side transfer member 103 of the second clutch C-2 is linked tothe carrier CR2 on the side facing the planetary gear set DP, it ispossible to eliminate a member that encloses the planetary gear unit PU.Thereby, the automatic transmission 1 ₁₃ can be made more radiallycompact. In addition, it is possible to shorten the transfer member thatrequires a high rigidity, to reduce the weight, and to improve thecontrollability of the automatic transmission 1 ₁₃. Furthermore, thestructure allows lubricating oil to be readily discharged where needed,and the cooling performance to be ensured. In addition, the assembly ofthe automatic transmission 1 ₁₃ can be simplified. Furthermore, becausethe working oil for the clutches can be supplied from support wall 120due to the configuration of each of the clutches, it is possible toreduce the number of seal rings, to reduce the sliding resistance of theseal rings, and to improve the power transfer efficiency of theautomatic transmission 1 ₁₃.

In addition, because the hydraulic servo 50 of the fourth clutch C-4 islocated axially intermediate the planetary gear unit PU and theplanetary gear set DP, axially adjacent the planetary gear set DP, it ispossible to use in common portions of the carrier CR1 and the clutchdrum 52 of the hydraulic servo 50 of the fourth clutch C-4 (that is, theclutch drum 52 and the side plate of the carrier CR1), and therebyreduce the size and weight.

Furthermore, because the hydraulic servo 30 of the second clutch C-2 islocated on the side of the planetary gear set DP that is axiallyopposite the planetary gear unit PU, it is possible to supply theworking oil to the hydraulic servo 30 of the second clutch C-2 from anoil duct in the boss 3 b. Thereby, in comparison to a structure in whichthe working oil is supplied from an oil duct in the input shaft 12, itis possible to reduce the number of seal rings, to reduce the slidingresistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₁₃.

In addition, because the hydraulic servo 40 of the third clutch C-3 islocated axially intermediate the planetary gear unit PU and theplanetary gear set DP, as compared to a structure in which the hydraulicservo 40 of the third clutch C-3 is located on the side of the planetarygear set DP that is axially opposite the planetary gear unit PU, it ispossible to shorten the distance between the third clutch C-3 and theplanetary gear unit PU, and it is possible to shorten the output sidetransfer member 101 of the third clutch C-3, which must be strong inorder to transfer high torque. Thereby, it is possible to reduce theweight and to improve the controllability of the automatic transmission1 ₁₃.

Furthermore, because the hydraulic servo 20 of the first clutch C-1 islocated on the side of the planetary gear set DP that is axiallyopposite the planetary gear unit PU, it is possible to supply theworking oil to the hydraulic servo 20 of the first clutch C-1 from anoil duct provided in the boss 3 b. Thereby, in comparison to a structurein which the working oil is supplied from an oil duct in the input shaft12, it is possible to reduce the number of seal rings, and to reduce thesliding resistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₁₃.

A first brake B-1 selectively locks the sun gear S2 against rotation,and the hydraulic servo 60 of the first brake B-1 is located on the sideof the counter gear 15 that is axially opposite the planetary gear unitPU, and the output side transfer member of the first brake B-1 is linkedto the sun gear S2 through the inner circumferential side of the countergear 15. Therefore, the output side transfer member of the first brakeB-1 and the sun gear S2 can be linked without making these memberscomplicated, and the automatic transmission 1 ₁₃ can be made morecompact.

The transfer member 103 of the output side of the second clutch C-2 islinked to the carrier CR2 radially outward of the transfer members 101,102 of the output side of the third and first clutches C-3, C-1. Theintermediate shaft 13, which is the transfer member of the output sideof the fourth clutch C-4, and the transfer member 101 of the output sideof the third clutch C-3 are linked to the sun gear S2, and theintermediate shaft 13, the transfer member 101, and the sun gear S2,which rotate integrally, are arranged on the inner side of the transfermember 102. Therefore, the intermediate shaft 13, which rotates fasterthan the transfer member 103 of the output side of the second clutchC-2, is further radially inward than the transfer member 102 of theoutput side of the first clutch C-1, which is on the inner side of thetransfer member 103 of the output side of the second clutch C-2. Thus,it is possible to make the diameter of the intermediate shaft 13 smallerthan the diameter of the transfer member, and to reduce the weight ascompared to a structure wherein the intermediate shaft 13 is on theouter side. In addition, because inertia is reduced as compared to astructure in which intermediate shaft 13 is on the outer side, it ispossible to improve the controllability of the automatic transmission 1₁₃.

The third and first clutches C-3, C-1 are disposed on the side of theplanetary gear set DP. The transfer members 101, 102 of the output sidesof the third and first clutches C-3, C-1 are respectively linked to thesun gear S2 and the sun gear S3. The fourth clutch C-4 is disposed onthe side of the planetary gear set DP. The intermediate shaft 13, whichis the transfer member of the output side of the fourth clutch C-4, islinked to the sun gear S2, the second clutch C-2 is on the side of theplanetary gear set DP, the transfer member 103 of the output side of thesecond clutch C-2 extends around the outer circumferences of thetransfer members 101, 102 of output sides of the third and firstclutches C-3, C-1 to link with the carrier CR2. Because the intermediateshaft 13, which is the transfer member of the output side of the fourthclutch C-4 and which rotates faster than the transfer member 103 of theoutput side of the second clutch C-2, is disposed radially inward, thediameter of the intermediate shaft 13, can be made smaller than thediameter of the transfer member 103 of the output side of the secondclutch C-2, thereby reducing weight as compared to a structure in whichthe intermediate shaft 13 is disposed on the outer circumferential side.In addition, compared to the case in which it is disposed on the outercircumferential side, it is possible to reduce inertia, and thus improvethe controllability of the automatic transmission 1 ₁₃.

Furthermore, because the transfer member of the output side of thefourth clutch C-4 is directly linked to the carrier CR1 and a portion ofthe carrier CR1 forms a portion of the hydraulic servo 50 of the fourthclutch C-4, i.e. a portion of the clutch drum 52 and the side plate ofthe carrier CR1 are used in common, it is possible to reduce the sizeand weight.

The boss 3 b which extends from the side wall 3 a of the case 4 holdsthe sun gear S1 stationary, the transfer member of the input side of thesecond clutch C-2 is linked to the carrier CR1, a portion of thetransfer member of the input side of the second clutch C-2 forms aportion of a clutch drum 32 of the hydraulic servo 30 which is supportedon the boss 3 b axially intermediate the planetary gear set DP and theside wall 3 a. Therefore, it is possible to supply the working oil tothe hydraulic servo 30 of the third clutch C-3 from an oil duct c30 inthe boss 3 b. Thus, in comparison to a structure in which, for example,the hydraulic servo 30 of the second clutch C-2 is disposed around theinput shaft 12 spaced from the boss 3 b and the working oil is suppliedvia an oil duct in the input shaft 12, it is possible to shorten thelength of the oil duct by an amount equivalent to the length of the oilduct in the input shaft 12, and it is possible to improve thecontrollability of the automatic transmission 1 ₁₃.

In addition, because the hub member 111 of the first clutch C-1 islinked to the ring gear R1, because the transfer member 102 of theoutput side of the first clutch C-1 is linked to the sun gear S3,because a portion of the transfer member 102 of the output side of thefirst clutch C-1 forms the clutch drum 22 of the hydraulic servo 20 ofthe first clutch C-1, and because the hydraulic servo 20 is disposed onthe boss 3 b, axially intermediate the planetary gear set DP and thehydraulic servo 20 of the first clutch C-1, it is possible to supply theworking oil to the hydraulic servo 20 of the first clutch C-1 from anoil duct c20 in the boss 3 b. Thus, in comparison to a structure inwhich, for example, the hydraulic servo 20 of the first clutch C-1 isdisposed around the input shaft 12, spaced from the boss 3 b, and theworking oil is supplied via an oil duct in the input shaft 12, it ispossible to shorten the length of the oil duct by the length of an oilduct in the input shaft 12, and it is possible to improve thecontrollability of the automatic transmission 1 ₁₃.

Because counter gear 15, linked to the ring gear R3 of the planetarygear unit PU, is disposed on the side of the planetary gear unit PU thatis axially opposite the planetary gear set DP, and the multi-platebrakes are disposed radially outward of the planetary gear unit PU, incomparison to a structure in which, for example, the counter gear 15 isbetween the planetary gear unit PU and the planetary gear set DP, thehub member 117 of the second brake B-2 and the transfer member 103 ofthe output side of the second clutch C-2 are used in common to link tothe carrier CR2, and, in contrast to the case in which a band brake isdisposed around the outer circumference of the transfer member 103, itis possible to maintain compactness with multi-plate brakes.

Furthermore, because a counter shaft 81 is arranged in parallel with theinput shaft 12 and linked to the counter gear 15 to receive the outputrotation from the ring gear, it is possible to advantageously use theautomatic transmission 1 ₁₃ in an FF-type vehicle.

In addition, because the counter gear 15 is located on the side of theplanetary gear unit PU that is axially opposite the planetary gear setDP and is supported by the support member 120 a, it is possible toshorten the distance between the planetary gear set DP and the planetarygear unit PU, and to shorten the output side member 101 of the thirdclutch C-3 and the output side member 102 of the first clutch C-1, whichmust in particular be strong in order to transfer a high torque. It isthereby possible to reduce weight and to improve the controllability ofthe automatic transmission 1 ₁₃.

In addition, because the carrier CR1 is linked to the input shaft 12 onthe side of the planetary gear set DP facing the planetary gear set DPand linked to the clutch drum 32, which is the transfer member of theinput side of the second clutch C-2, on the side of the planetary gearset DP that is axially opposite the planetary gear unit PU, it ispossible to link the carrier CR1 and the input shaft 12 without makingthese members complicated and to make the automatic transmission 1 ₁₃more compact.

In addition, because the hub 116 of the first brake B-1 and the transfermember 104 are axially linked to the sun gear S2 on the side of theplanetary gear unit PU that is axially opposite the planetary gear setDP, it is possible to link the hub member 116 of the first brake B-1,the transfer member 104, and the sun gear S2 without making thesemembers complicated and to make the automatic transmission 1 ₁₃ morecompact.

In addition, because the planetary gear set DP includes thenon-rotatable sun gear S1, a carrier CR1 that rotatably supports thepinion gear P1 and the pinion gear P2 and is linked to the output shaft12, and a ring gear R1 that meshes with the pinion gear P2 and outputs areduced speed rotation, it is possible to output a reduced speedrotation, i.e. at a speed less than that of the input rotation of theinput shaft 12, from the ring gear R1.

Because the planetary gear unit PU is a Ravigneaux-type planetary gearunit PU that includes the sun gear S2, the sun gear S3, the short pinionP3 that meshes with the sun gear S3, the long pinion P4 that meshes withthe sun gear S2 and meshes with the short pinion P3, the carrier CR2that rotatably supports the short pinion P3 and the long pinion P4, andthe ring gear R3 that meshes with the long pinion P4, it is possible toprevent high speed rotation of each of the rotary elements and to obtainadvantageous gear ratios while enabling each of the rotary elements ofthe planetary gear unit PU and the output side members of each of theclutches and brakes to be linked without making these memberscomplicated.

The first forward speed is established by engaging the first clutch C-1and locking the second brake B-2; the second forward speed isestablished by engaging the first clutch C-1 and locking the first brakeB-1; the third forward speed is established by engaging the first clutchC-1 and the third clutch C-3; the fourth forward speed is established byengaging the first clutch C-1 and the fourth clutch C-4; the fifthforward speed is established by engaging the first clutch C-1 and thesecond clutch C-2; the sixth forward speed is established by engagingthe second clutch C-2 and the fourth clutch C4; the seventh forwardspeed is established by engaging the second clutch C-2 and the thirdclutch C-3; the eighth forward speed is established by engaging thesecond clutch C-2 and locking the first brake B-1; and reverse speedsare established by engaging the third clutch C-3 or the fourth clutchC-4 and locking the second brake B-2.

In a velocity diagram in which the respective speeds of the sun gear S2,the sun gear S3, the carrier CR2, and the ring gear R3 of the planetarygear unit PU are shown on the ordinate, and the corresponding gearratios of the sun gear S2, the sun gear S3, and carrier CR2, and thering gear R3 are shown on the abscissa, the sun gear S2 is positioned atthe farthest left end of the ordinate and, in sequence to the rightthereof, are the carrier CR2, the ring gear R3 that is linked to thecounter gear 15, and the sun gear S3.

Fourteenth Embodiment

Next, a fourteenth embodiment, in which a portion of the twelfthembodiment described above has been modified, will be explained withreference to FIG. 19 which is a cross-sectional view of automatictransmission 1 ₁₄. Features which are identical to those of theautomatic transmission 1 ₁₂ of the twelfth embodiment are denoted byidentical reference numerals, and explanation thereof is omitted.

In the automatic transmission 1 ₁₄ of the fourteenth embodiment, thearrangement of the input shaft 12, the intermediate shaft 13 and theengine is unchanged. However, the arrangement of the first throughfourth clutches C-1 to C-4, the first and second brakes B-1 to B-2, theplanetary gear set DP, the planetary gear unit PU, and the counter gear15 is substantially reversed. In other words, the speed change mechanism2 ₁₄ is substantially reversed 180° left-right.

The automatic transmission 1 ₁₄, the hydraulic servo 30 of the secondclutch C-2 and the hydraulic servo 20 of the first clutch C-1 arelocated on the side of the planetary gear set DP that is axiallyopposite the planetary gear unit PU, the hydraulic servo 40 of the thirdclutch C-3 is located axially intermediate the planetary gear set DP andthe planetary gear unit PU, and the counter gear 15, the hydraulic servo50 of the fourth clutch C-4, and the hydraulic servo 60 of the firstbrake B-1 are located on the side of the planetary gear unit PU that isaxially opposite the planetary gear set DP.

In the automatic transmission 1 ₁₄, because the fourth clutch C-4 isinterposed in the transfer path to connect the input shaft 12 and thesun gear S2, the second clutch C-2 is interposed in the transfer path toconnect the carrier CR1 and the carrier CR2, and the output sidetransfer member 103 of the second clutch C-2 is linked to the side ofthe carrier CR2 axially facing the planetary gear set DP, it is possibleto eliminate a member that encloses the planetary gear unit PU. Thereby,the automatic transmission 1 ₁₄ can be made more radially compact. Inaddition, it is possible to shorten the transfer member that requires ahigh rigidity, to reduce the weight, and it to improve thecontrollability of the automatic transmission 1 ₁₄. Furthermore, thestructure allows lubricating oil to be readily discharged where needed,and the cooling performance to be ensured. In addition, the assembly ofthe automatic transmission 1 ₁₄ can be simplified. Furthermore, becausethe working oil for the clutches can be supplied from support wall 120due to the configuration of each of the clutches, it is possible toreduce the number of seal rings, to reduce the sliding resistance of theseal rings, and to improve the power transfer efficiency of theautomatic transmission 1 ₁₄.

In addition, because the hydraulic servo 30 of the second clutch C-2 islocated on the side of the planetary gear set DP that is axiallyopposite the planetary gear unit PU, it is possible to supply theworking oil to the hydraulic servo 30 of the second clutch C-2 from anoil duct in the boss 3 b. Thereby, in comparison with a structure inwhich the working oil is supplied from an oil duct in the input shaft12, it is possible to reduce the number of seal rings, to reduce thesliding resistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₁₄.

Furthermore, because the hydraulic servo 50 of the fourth clutch C4 isdisposed on the side of the planetary gear unit PU that is axiallyopposite the planetary gear set DP, it is possible to dispose thefriction plates 51 of the fourth clutch C-4 more radially outward and toenlarge the surface area of the friction plates 51, and thus, it ispossible to provide transfer of sufficient torque, while reducing thenumber of friction plates. Furthermore, the working oil is supplied tothe hydraulic servo 50 of the fourth clutch C-4 from an oil duct in theboss 3 d, whereby, in comparison to a structure in which the working oilis supplied from an oil duct in the input shaft 12, it is possible toreduce the number of seal rings, to reduce the sliding resistance of theseal rings, and to improve the power transfer efficiency of theautomatic transmission 1 ₁₄.

In addition, because the hydraulic servo 40 of the third clutch C-3 islocated axially intermediate the planetary gear unit PU and theplanetary gear set DP, in comparison to a structure in which thehydraulic servo 40 of the third clutch C-3 is located on the side of theplanetary gear set DP that is axially opposite the planetary gear unitPU, it is possible to shorten the distance between the third clutch C-3and the planetary gear unit PU, and to shorten the output side transfermember 101 of the third clutch C-3, which must be strong in order totransfer high torque. Thereby, it is possible to reduce the weight, andto improve the controllability of the automatic transmission 1 ₁₄.

Furthermore, because the hydraulic servo 20 of the first clutch C-1 islocated on the side of the planetary gear set DP that is axiallyopposite the planetary gear unit PU, it is possible to supply theworking oil to the hydraulic servo 20 of the first clutch C-1 from anoil duct in the boss 3 b. Thereby, in comparison to a structure in whichworking oil is supplied from an oil duct in the input shaft 12, it ispossible to reduce the number of seal rings, to reduce the slidingresistance of the seal rings, and to improve the power transferefficiency of the automatic transmission 1 ₁₄ for an engine.

In addition, a first brake B-1 selectively locks the sun gear S2 againstrotation, the hydraulic servo 60 of the first brake B-1 is located onthe side of the counter gear 15 that is axially opposite the planetarygear set DP, and the locking force transfer member of the first brakeB-1 axially extends on the radially inner side to link to the sun gearS2. Therefore, it is possible to link the locking force transfer memberof the first brake B-1 and the sun gear S2 without making these memberscomplicated, and to make the automatic transmission 1 ₁₄ more compact.

In the automatic transmission 1 ₁₄ according to the present invention asexplained above, the transfer member 103 of the output side of thesecond clutch C-2 extends around the outer circumference of the transfermembers 101, 102 of the output sides of the third and first clutchesC-3, C-1 to link with the carrier CR2, the transfer member 104 of theoutput side of the fourth clutch C-4 and the transfer member 101 arelinked to the sun gear S2, and the transfer member 104, the transfermember 101, and the sun gear S2, which rotate integrally, are disposedon the radially inner side of the transfer member 102. Therefore, thetransfer member 104, which rotates faster than the transfer member 103,is more radially inward than the transfer member 102, which is on theradially inner side of the transfer member 103. Thus, it is possible tomake the diameter of the transfer member 104 smaller than the diameterof the transfer member 103, and to reduce the weight as compared to astructure in which the transfer member 104 is on the radially outerside. In addition, because the inertia is reduced in comparison to astructure in which transfer member 104 is disposed on the radially outerside, it is possible to improve the controllability of the automatictransmission 1 ₁₄.

In addition, the third and first clutches C-3, C-1 are disposed on theside of the planetary gear set DP, the transfer members 101, 102 of theoutput side of the third and first clutches C-3, C-1 are respectivelylinked to the sun gear S2 and the sun gear S3, the fourth clutch C4 islocated on the side of the planetary gear unit PU that is axiallyopposite the planetary gear set DP, the transfer member 104 is linked tothe sun gear S2, the second clutch C-2 is disposed on the planetary gearset DP side, and the transfer member 103 extends around the outercircumferences of the transfer members 101, 102 to link with carrierCR2. Thereby, the diameter of the transfer member 104 can be madesmaller than the diameter of the transfer member 103. Because thetransfer member 104, which rotates faster than the transfer member 103,is disposed on the radially inner side, it is possible to reduce theweight as compared to a structure in which the transfer member 104 isdisposed on the radially outer side. In addition, compared to the casein which the transfer member 104 is disposed on the outside, it ispossible to reduce the inertia, and to thereby improve thecontrollability of the automatic transmission 1 ₁₄.

In addition, in comparison to a structure in which the hydraulic servo50 of the fourth clutch C-4 is located axially between the planetarygear unit PU and the planetary gear set DP, it is possible to disposethe friction plates 51 of the fourth clutch C-4 more radially outwardand to increase the area of the friction plates and, thus, it ispossible to transfer sufficient torque while reducing the number of thefriction plates 51. Furthermore, it is possible to shorten the distancebetween the third and first clutches C-3, C-1 and the planetary gearunit PU, and to shorten the transfer members 101, 102 of the output sideof the third and first clutches C-3, C-1, which must be strong in orderto transfer a high torque. Thereby, it is possible to reduce the weightand to improve the controllability of the automatic transmission 1 ₁₄.

Because the working oil is supplied to the hydraulic servo 50 of thefourth clutch C-4 from an oil duct c50 in the boss 3 b, in comparison toa structure in which the working oil is supplied from an oil duct in theinput shaft 12, it is possible to reduce the number of seal rings, toreduce the sliding resistance of the seal rings, and to improve thepower transfer efficiency of the automatic transmission 1 ₁₄.

In addition, because the transfer member of the input side of the fourthclutch C4 is linked to the input shaft 12 and the intermediate shaft 13through the inner circumferential side of the planetary gear unit PU anda portion of the transfer member of the input side of the fourth clutchC4 forms the clutch drum 52 of the hydraulic servo 50 of the fourthclutch C-4, in contrast to a structure in which the transfer member ofthe output side of the fourth clutch C4 forms the clutch drum of thehydraulic servo 50, the clutch drum 52 can be used as a member totransfer power from the input shaft 12, and thus, it is possible to makethe transfer member more axially compact.

In addition, because of provision of boss 3 b which holds the sun gearS1 stationary, because the transfer member of the input side of thesecond clutch C-2 is linked to the carrier CR1, because a portion of thetransfer member of the input side of the second clutch C-2 forms aportion of clutch drum 32 of the hydraulic servo 30 of the second clutchC-2, and because the hydraulic servo 30 is supported on the boss 3 baxially intermediate the planetary gear set DP and the side wall 3 a, itis possible to supply the working oil to the hydraulic servo 30 of thethird clutch C-3 from an oil duct c30 in the boss 3 b. Thus, incomparison to a structure in which, for example, the hydraulic servo 30of the second clutch C-2 is disposed around the input shaft 12,separated from the boss 3 b, and the working oil is supplied via an oilduct in the input shaft 12, it is possible to shorten the length of theoil duct by the length of an oil duct in the input shaft 12, therebyimproving the controllability of the automatic transmission 1 ₁₄.

In addition, because the hub 111 of the first clutch C-1 is linked tothe ring gear R1, the transfer member 102 of the output side of thefirst clutch C-1 is linked to the sun gear S3, a portion of the transfermember 102 of the output side of the first clutch C-1 forms the clutchdrum 22 of the hydraulic servo 20 of the first clutch C-1, and thehydraulic servo 20 is supported on the boss 3 b axially intermediate theplanetary gear set DP and the hydraulic servo 20 of the first clutchC-1, it is possible to supply the working oil to the hydraulic servo 20of the first clutch C-1 from an oil duct c20 in the boss 3 b. Thus, incomparison to a structure in which, for example, the hydraulic servo 20of the first clutch C-1 is disposed around the input shaft 12, separatedfrom the boss 3 b, and the working oil is supplied via an oil duct inthe input shaft 12, it is possible to shorten the length of the oil ductby an amount equivalent to the length of an oil duct in the input shaft12, thereby improving the controllability of the automatic transmission1 ₁₄.

Further, because counter gear 15 is located on the side of the planetarygear unit PU that is axially opposite the planetary gear set DP, becausethe second brake B-2 is a multi-plate brake with a plurality of frictionplates 71, and the multi-plate brakes are disposed on the outercircumferential side of the planetary gear unit PU, in contrast with astructure in which, for example, the counter gear 15 is between theplanetary gear unit PU and the planetary gear set DP, the hub 117 of thesecond brake B-2 can use the transfer member 103 of the output side ofthe second clutch C-2 to link to the carrier CR2, and, for example, incomparison to a structure in which a band brake is disposed around theouter circumference of the transfer member 103, it is possible to locatethe multi-plate brakes radially outward of the planetary gear unit PU,to maintain compactness and to make the brakes multi-plate.

Furthermore, because a counter shaft 81 is arranged in parallel with theinput shaft 12 and linked to the counter gear 15 for receipt of theoutput rotation from the ring gear R3, the automatic transmission 1 ₁₄is advantageously used in an FF-type vehicle.

In addition, because the counter gear 15 is located on the side of theplanetary gear unit PU that is axially opposite the planetary gear setDP and is supported on the support member 120 a that is linked to thesupport wall 120 that extends from the case 4, it is possible to shortenthe distance between the planetary gear set DP and the planetary gearunit PU, and it is possible to shorten the output side member 101 of thethird clutch C-3 and the output side member 102 of the first clutch C-1,which must in particular be strong in order to transfer a high torque.Thereby, it is possible to reduce the weight and to improve thecontrollability of the automatic transmission 1 ₁₄.

Further, because the carrier CR1 is linked to the input shaft 12 on theside of the planetary gear set DP side facing the planetary gear unit PUand is linked to the hub member 114, which is the transfer member of theinput side of the second clutch C-2, on the side of the planetary gearunit PU that is axially opposite the planetary gear set DP, it ispossible to link the carrier CR1, the transfer member 114 of the inputside of the second clutch C-2, and the input shaft 12 without makingthese members complicated, and to thereby make the automatictransmission 1 ₁₄ more compact.

In addition, because the hub member 116 of the first brake B-1 and thetransfer member 104 that is linked thereto are axially linked to the sungear S2 on the side of the planetary gear unit PU that is axiallyopposite the planetary gear set DP, it is possible to link the hubmember 116 of the first brake B-1, the transfer member 104, and the sungear S2 without making these members complicated, and it is possible tomake the automatic transmission 1 ₁₄ more compact.

Because the planetary gear set DP includes the sun gear S1, which isheld stationary, a carrier CR1 that rotatably supports the pinion gearP1 and the pinion gear P2 and is linked to the output shaft 12, and aring gear R1 that meshes with the pinion gear P2 and outputs a reducedspeed rotation, it is possible to output a reduced speed rotation fromthe ring gear R1, i.e. at a speed less than that of the input rotationof the input shaft 12.

In addition, because the planetary gear unit PU is a Ravigneaux-typeplanetary gear unit PU that includes the sun gear S2, the sun gear S3,the short pinion P3 that meshes with the sun gear S3, the long pinion P4that meshes with the sun gear S2 and meshes with the short pinion P3,the carrier CR2 that selectively rotatably supports the short pinion P3and the long pinion P4, and the ring gear R3 that meshes with the longpinion P4, it is possible to prevent high speed rotation of each of therotary elements and to provide advantageous gear ratios while enablingeach of the rotary elements of the planetary gear unit PU and the outputside members of each of the clutches and brakes to be linked withoutmaking these members complicated.

The first forward speed is established by engaging the first clutch C-1and locking the second brake B-2; the second forward speed isestablished by engaging the first clutch C-1 and locking the first brakeB-1; the third forward speed is established by engaging the first clutchC-1 and the third clutch C-3; the fourth forward speed is established byengaging the first clutch C-1 and the fourth clutch C-4; the fifthforward speed is established by engaging the first clutch C-1 and thesecond clutch C-2; the sixth forward speed is established by engagingthe second clutch C-2 and the fourth clutch C-4; the seventh forwardspeed is established by engaging the second clutch C-2 and the thirdclutch C-3; the eighth forward speed is established by engaging thesecond clutch C-2 and locking the first brake B-1; and reverse speedsare established by engaging the third clutch C-3 or the fourth clutchC-4 and locking the second brake B-2.

In a velocity diagram in which the respective speeds of the sun gear S2,the sun gear S3, the carrier CR2, and the ring gear R3 of the planetarygear unit PU are shown on the ordinate, and the corresponding gearratios of the sun gear S2, the sun gear S3, and carrier CR2, and thering gear R3 are shown on the abscissa, the sun gear S2 is positioned atthe farthest left end of the ordinate and, extending in sequence to theright thereof, are the carrier CR2, the ring gear R3 that is linked tothe counter gear 15, and the sun gear S3.

While in the first through fourteenth embodiments described above, theautomatic transmission is described as including a torque converter 7, astart-up clutch may be used instead of torque converter 7.

Moreover, the automatic transmission 1 of the first through fourteenthembodiments is not limited to use in an FF-type vehicle. For example,the present invention may be applied to an automatic transmission for avehicle that is used in a four-wheel drive-type vehicle and to anautomatic transmission in a hybrid vehicle.

Further, while the fifth and tenth embodiments have a one-way clutch F-1whereby the automatic transmission 1 establishes the first forward speedrelatively smoothly, but it is not necessary to provide a one-way clutchF-1 and, instead, the first forward speed may be established by engagingthe second brake B-2. Conversely, while the first through fourthembodiments, the sixth through ninth embodiments, and the elevenththrough fourteenth embodiments, as described, do not include a one-wayclutch F-1, a one-way clutch F-1 may be included in these embodiments toestablish the first forward speed relatively smoothly.

In addition, while the first through fourteenth embodiments aredescribed as including the planetary gear set DP that outputs a reducedspeed rotation and which is a double pinion planetary gear set in whichthe rotation of the sun gear S1 is held stationary, the rotation of theinput shaft 12 is input to the carrier CR1, and the ring gear R1 outputsthe reduced speed rotation, instead, the planetary gear set may be adouble pinion planetary gear in which, for example, the ring gear R1 isheld stationary, the rotation of the input shaft 12 is output to thecarrier CR1, and the reduced speed rotation is output from the sun gearS1, or any other planetary gear structure that outputs a reduced speedrotation.

The automatic transmission according to the present invention may beused in any vehicle such as a passenger vehicle, a truck, a bus, and thelike, and in particular, in vehicles that require multi-speed automatictransmissions in order to improve fuel economy and/or reductions inweight and improved controllability.

1. An automatic transmission for a vehicle, comprising: a case having aside wall; an input shaft; a speed reduction planetary gear set thatcomprises a stationary element that is held stationary by the case, aninput rotary element that receives the input rotation of the inputshaft, and a speed reduction rotary element that outputs a reduced speedrotation at a speed less than that of the input rotation; a planetarygear unit that includes first, second, third, and fourth rotary elementsthat are arranged in rotational speed relationships according to theirgear relationships; a first input transfer clutch, having input side andoutput side transfer members, for selective transfer of the inputrotation to the first rotary element; a second input transfer clutch,having input side and output side transfer members, for selectivetransfer of the input rotation to the third rotary element; a firstspeed reduction transfer clutch, having input side and output sidetransfer members, for selective transfer of a reduced speed rotationthrough the speed reduction planetary gear set to the first rotaryelement; a second speed reduction transfer clutch, having input side andoutput side transfer members, for selective transfer of a reduced speedrotation through the speed reduction planetary gear set to the secondrotary element; a first brake for selectively stopping rotation of thefirst rotary element by locking the first rotary element to the case;and a second brake for selectively stopping rotation of the third rotaryelement by locking the third rotary element to the case; and wherein theautomatic transmission outputs output rotation at the fourth rotaryelement; wherein the first and second speed reduction transfer clutchesare disposed on the speed reduction planetary gear set side relative tothe planetary gear set; wherein the output side transfer members of thefirst and second speed reduction transfer clutches are respectivelylinked to the first rotary element and the second rotary element;wherein the first input transfer clutch is disposed on the speedreduction planetary gear set side relative to the planetary gear unitand its output side transfer member is linked to the first rotaryelement; wherein the second input transfer clutch is disposed on thespeed reduction planetary gear set side relative to the planetary gearunit and its output side transfer member extends around the outercircumferences of the output side transfer members of the first andsecond speed reduction transfer clutches to link with the third rotaryelement; and wherein: a first forward speed is established by engagingthe second speed reduction transfer clutch and locking the second brake;a second forward speed is established by engaging the second speedreduction transfer clutch and locking the first brake; a third forwardspeed is established by engaging the second speed reduction transferclutch and the first speed reduction transfer clutch; a fourth forwardspeed is established by engaging the second speed reduction transferclutch and the first input transfer clutch; a fifth forward speed isestablished by engaging the second speed reduction transfer clutch andthe second input transfer clutch; a sixth forward speed is establishedby engaging the second input transfer clutch and the first inputtransfer clutch; a seventh forward speed is established by engaging thesecond input transfer clutch and the first speed reduction transferclutch; an eighth forward speed is established by engaging the secondinput transfer clutch and locking the first brake; and a reverse speedis established by engaging the first speed reduction transfer clutch orthe first input transfer clutch, and locking the second brake.
 2. Theautomatic transmission for a vehicle according to claim 1, furthercomprising: a first hydraulic servo for operating the first inputtransfer clutch; and wherein the first input transfer clutch has aninput side transfer member directly linked to the input rotary elementand a portion of the input rotary element forms a portion of the firsthydraulic servo of the first input transfer clutch.
 3. The automatictransmission for a vehicle according to claim 1, further comprising: afirst hydraulic servo, including a drum, for operating the second inputtransfer clutch; a boss extending from the side wall of the case andsupporting the stationary element and fixing the stationary elementagainst rotation; and wherein the input side transfer member of thesecond input transfer clutch is linked to the input rotary element;wherein a portion of the input side transfer member of the second inputtransfer clutch forms the clutch drum of the first hydraulic servo; andwherein the first hydraulic servo is disposed around the boss axiallyintermediate the speed reduction planetary gear set and the side wall.4. The automatic transmission for a vehicle according to claim 3,further comprising: a second hydraulic servo, including a drum, foroperating the second speed reduction transfer clutch; wherein the inputside transfer member of the second speed reduction transfer clutch islinked to the reduced speed rotary element; wherein the output sidetransfer member of the second speed reduction transfer clutch is linkedto the second rotary element; wherein a portion of the output sidetransfer member of the second speed reduction transfer clutch forms theclutch drum of the second hydraulic servo; and wherein the secondhydraulic servo is disposed around the boss axially intermediate thespeed reduction planetary gear set and the first hydraulic servo.
 5. Theautomatic transmission for a vehicle according to claim 4, furthercomprising: a counter gear linked to the fourth rotary element of theplanetary gear unit; and wherein the planetary gear unit and the speedreduction planetary gear set are disposed on opposite sides of thecounter gear; and wherein the second brake is a multi-plate brakecomprising a plurality of friction plates and is located radiallyoutward of the planetary gear unit.
 6. The automatic transmission for avehicle according to claim 3, further comprising: a counter gear linkedto the fourth rotary element of the planetary gear unit to form aconnection; and wherein the planetary gear unit and the speed reductionplanetary gear set are disposed on opposite sides of the counter gear;and wherein the second brake is a multi-plate brake comprising aplurality of friction plates and is located radially outward of theplanetary gear set.
 7. The automatic transmission for a vehicleaccording to claim 1, further comprising: a first hydraulic servo,including a drum, for operating the second input transfer clutch; acounter gear linked to the fourth rotary element and located axiallyintermediate the planetary gear unit and the speed reduction planetarygear set; and a support wall extending radially inward from the case andhaving a distal end with a support member appended thereto andsupporting the counter gear; and wherein the input side transfer memberof the second input transfer clutch extends around the outercircumferences of the first and second speed reduction transfer clutchesto link with the input rotary member; wherein a portion of the outputside transfer member of the second input transfer clutch forms theclutch drum of the first hydraulic servo; and wherein the firsthydraulic servo is disposed around the support member axiallyintermediate the speed reduction planetary gear set and the countergear.
 8. The automatic transmission for a vehicle according to claim 7,further comprising: a second hydraulic servo, including a drum, foroperating the first speed reduction transfer clutch; a third hydraulicservo, including a drum, for operating the second speed reductiontransfer clutch; a boss extending from the side wall of the case andsupporting the stationary element while holding the stationary elementstationary; and wherein the input side transfer member of the firstspeed reduction transfer clutch is linked to the reduced speed rotaryelement; wherein a portion of the input side transfer member of thefirst speed reduction transfer clutch forms the clutch drum of thesecond hydraulic servo; wherein the second hydraulic servo is disposedaround the boss axially intermediate the speed reduction planetary gearset and the side wall; wherein the input side transfer member of thesecond speed reduction transfer clutch is linked to the input sidetransfer member of the first speed reduction transfer clutch; wherein aportion of the input side transfer member of the second speed reductiontransfer clutch forms the clutch drum of the third hydraulic servo; andwherein the third hydraulic servo is disposed around the support memberaxially intermediate the speed reduction planetary gear and the firsthydraulic servo.
 9. The automatic transmission for a vehicle accordingto claim 1, wherein a counter gear linked to the fourth rotary elementand a second shaft is arranged in parallel with the input shaft and islinked via the counter gear to the fourth rotary element to receive theoutput rotation.
 10. The automatic transmission for a vehicle accordingto claim 9, further comprising: a wall member extending radially inwardfrom the case and a support member appended to the inner circumferenceof the wall member; and wherein the counter gear is located axiallyintermediate the planetary gear unit and the speed reduction planetarygear set and is supported on the support member.
 11. The automatictransmission for a vehicle according to claim 9, further comprising: awall member extending radially inward from the case and a support memberappended to the inner circumference of the wall member; wherein thecounter gear is supported by the support member; and wherein the countergear and the speed reduction planetary gear set are disposed on oppositesides of the planetary gear unit.
 12. The automatic transmission for avehicle according to claim 1, wherein a first side of the input rotaryelement, facing the planetary gear unit, is linked to the input shaft,and a second side of the input rotary element, opposite the first side,is linked to the input side transfer member of the second input transferclutch.
 13. The automatic transmission for a vehicle according to claim1, wherein the first brake has a locking force transfer member linked toa first side of the first rotary element that is axially opposite asecond side of the first rotary element facing the speed reductionplanetary gear set.
 14. The automatic transmission for a vehicleaccording to claim 1, wherein: the stationary element of the speedreduction planetary gear set comprises a first sun gear; the inputrotary element of the speed reduction planetary gear set is linked tothe input shaft and comprises a first carrier that rotatably supports afirst pinion gear that meshes with the first sun gear and a secondpinion gear that meshes with the first pinion gear; and the reducedspeed rotary element of the speed reduction planetary gear set comprisesa first ring gear that meshes with the second pinion gear and outputsthe reduced speed rotation.
 15. The automatic transmission for a vehicleaccording to claim 1, wherein: the planetary gear set is a Ravigneauxplanetary gear set that comprises a second sun gear, a third sun gear, athird pinion gear that meshes with the third sun gear, a fourth piniongear that meshes with the second sun gear and meshes with the thirdpinion gear; a second carrier that rotatably supports the third piniongear and the fourth pinion gear; and a second ring gear that meshes withthe fourth pinion gear; the first rotary element comprises the secondsun gear; the second rotary element comprises the third sun gear; thethird rotary element comprises the second carrier; and the fourth rotaryelement comprises the second ring gear.